EP2016349B1 - Heat pump - Google Patents
Heat pump Download PDFInfo
- Publication number
- EP2016349B1 EP2016349B1 EP06724016A EP06724016A EP2016349B1 EP 2016349 B1 EP2016349 B1 EP 2016349B1 EP 06724016 A EP06724016 A EP 06724016A EP 06724016 A EP06724016 A EP 06724016A EP 2016349 B1 EP2016349 B1 EP 2016349B1
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- EP
- European Patent Office
- Prior art keywords
- water
- working
- pressure
- evaporator
- drain
- Prior art date
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Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D15/00—Other domestic- or space-heating systems
- F24D15/04—Other domestic- or space-heating systems using heat pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
- F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B27/00—Machines, plants or systems, using particular sources of energy
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D2200/00—Heat sources or energy sources
- F24D2200/11—Geothermal energy
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/06—Heat pumps characterised by the source of low potential heat
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/007—Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/0071—Evaporators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
- F28F21/06—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A40/00—Adaptation technologies in agriculture, forestry, livestock or agroalimentary production
- Y02A40/90—Adaptation technologies in agriculture, forestry, livestock or agroalimentary production in food processing or handling, e.g. food conservation
- Y02A40/963—Off-grid food refrigeration
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B10/00—Integration of renewable energy sources in buildings
- Y02B10/40—Geothermal heat-pumps
Definitions
- the present invention relates to heat pumps and more particularly to heat pumps that can be used for building heating and especially for heating buildings of smaller building units, such as single-family homes, semi-detached houses or terraced houses.
- Fig. 8 shows a known heat pump, as in " Technical Thermodynamics ", Theoretical Foundations and Practical Applications, 14th revised edition, Hanser Verlag, 2005, pages 278 - 279 , is described.
- the heat pump includes a closed circuit in which a working fluid such as R 134a circulates. About a first heat exchanger 80 and the evaporator so much heat is removed from the soil or groundwater that the working fluid evaporates. The now high-energy working fluid is sucked from the compressor via the suction line. In the compressor 81, it is compressed, thereby increasing pressure and temperature. This compression is performed by a reciprocating compressor. The compressed and under high temperature working fluid now passes into the second heat exchanger 82, the condenser.
- the working medium serves as an energy transporter to pick up heat from the ground or groundwater and deliver it to the heating circuit in the condenser.
- the second law is the Thermodynamics fulfilled, in which it is said that heat or energy from "self” can only be transferred from the higher temperature level to the lower temperature level, and that conversely this can only happen by external energy supply, here the drive work of the compressor.
- Fig. 7 shows a typical h, log p diagram (h is the enthalpy, p the pressure of a substance). Between point 4 and point 1 in the diagram of Fig. 7 an isobaric evaporation of the working fluid takes place at low values for the pressure and the temperature (p 1 , T 1 ). Here, the heat Q 81 is supplied.
- the adiabatic throttling of the working fluid then takes place from the high pressure p 2 to the low pressure p 1 .
- a part of the liquid working fluid evaporates and the temperature decreases to the evaporation temperature T 1 .
- the energies and characteristics of this process can be calculated by means of enthalpies and illustrated as in Fig. 7 is shown.
- the working fluid of the heat pump thus takes in the evaporator heat from the environment, ie air, water, sewage or soil, on.
- the condenser serves as a heat exchanger for heating a heating medium.
- the temperature T 1 is slightly below the ambient temperature, the temperature T 2 considerably, the temperature T 2 'slightly above the required heating temperature. The higher the required temperature difference, the more work the compressor must apply. It is therefore desirable to keep the temperature increase as small as possible.
- the working fluid liquefies.
- the length of the section 2-3 represents the useful heat Q.
- the relaxation takes place and from point 4 to point 1, the evaporation of the working substance, the distance 4-1 reproduces the heat extracted from the heat source.
- the amounts of heat and work can be taken as stretches in the h, log p diagram. Pressure losses in valves, the pressure and suction lines, the compressor, etc. deform the ideal course of the cycle in the h, log p diagram and reduce the effectiveness of the entire process.
- the aspirated working vapor initially has a lower temperature than the cylinder wall of the compressor and absorbs heat from it.
- the temperature of the working-material vapor finally increases above that of the cylinder wall, so that the working-substance vapor gives off heat to the cylinder wall.
- the piston again sucks in steam and compressed, the temperature of the piston wall is initially again fallen below and then exceeded, resulting in permanent losses.
- overheating of the aspirated working fluid will be necessary and necessary so that the compressor does not suck liquid agent.
- a disadvantage is in particular the heat exchange with the oil circuit of the reciprocating compressor, which is indispensable for lubrication.
- the liquefied low-temperature working fluid at the condenser outlet would have to be relieved by an ideal cycle through an engine, such as a turbine, to utilize the excess of energy that existed against the temperature and pre-compression conditions. For reasons of this required large expense, this measure is omitted and the pressure of the working fluid is abruptly reduced by the throttle 83 to the low pressure and the low temperature. The enthalpy of the working substance remains approximately the same. Due to the sudden reduction in pressure, the working fluid must partially evaporate in order to lower its temperature. The necessary heat of evaporation comes from the excess temperature located working fluid, so it is not removed from the heat source. The totality of the relaxation in the choke 83 ( Fig. 8 ) losses are referred to as relaxation losses.
- R134a which has CF 3 -CH 2 F as its chemical formula. This is a working fluid that is no longer harmful to the ozone layer, but has a 1000 times greater effect than carbon dioxide in terms of the greenhouse effect.
- the working fluid R134a is popular because it has a relatively large enthalpy difference of about 150 kJ / kg.
- a disadvantage of existing heat pumps is therefore in addition to the fact of the harmful working fluid and the fact that due to the many losses in the heat pump cycle, the efficiency of the heat pump is typically not more than a factor of 3. In other words, about 2 times the energy used for the compressor can be taken from the heat source, such as groundwater or soil.
- the efficiency in power generation is perhaps equal to 40%, so turns out that - in terms of the overall energy balance - a heat pump is doubtful in terms of utility.
- 120% 3 40% of heating energy is provided. After all, a conventional heating system with a burner achieves efficiencies of 90 - 95%, ie with a high technical and thus financial expense only an improvement of 25 - 30% is achieved.
- the DE 44 31 887 A1 discloses a heat pump system according to the preamble of claim 1 with a propeller-like rotary member consisting of a frusto-conical hub and a plurality of curved blades. Further, a mechanical steam compression heat pump system is provided which includes a pair of centrifugal compressors.
- the DE 10 2004 001 927 A1 discloses a method for heat recovery by means of a heat pump, in which a screw compressor with oil cooling and oil injection and water are used as refrigerant.
- the U.S. Patent No. 4,003,213 discloses a heat pump system according to the preamble of claim 1 which is suitable for the production of drinking water, and in which the thermal energy is generated from heat released by the freezing of water under vacuum at the triple point.
- the US 6,397,621 B1 discloses a heat pump installation according to the preamble of claim 1 having a cooling function in which the thermodynamic fluid used in the cycle is water. Dynamic compression in two separate compression stages is used, with the compression stages interconnected by at least one zone preventing overheating.
- the object of the present invention is to provide a more efficient heat pump concept.
- the present invention is based on the recognition that it is necessary to move away from climate-damaging working materials, and that instead normal water is an optimal working medium.
- water has a much larger ratio of enthalpy differences than the currently widely used R134a.
- the enthalpy difference which is crucial to the effectiveness of the heat pump process, is about 2500 kJ / kg for water, which is about 16 times the useful enthalpy difference of R134a.
- the compressor enthalpy to be used is only 4 to 6 times greater, depending on the operating point.
- the evaporator is designed such that it has an evaporation space in which the evaporation pressure is less than 20 hPa (hectopascal), so that the water evaporates at temperatures below 18 ° C and preferably below 15 ° C.
- Typical groundwater has temperatures in the northern hemisphere between 8 and 12 ° C, which requires pressures of less than 20 hPa, so that the groundwater evaporates in order to be able to achieve a lowering of the temperature of the groundwater and thus a heat extraction by the groundwater evaporation a building heating, such as a floor heating can be operated.
- Water is further advantageous in that water vapor occupies a very large volume, and thus to the compaction ten of the steam no longer on a displacement machine such as a piston pump or something similar must be resorted to, but a high-performance compressor in the form of a turbomachine such as a centrifugal compressor can be used, which is well manageable in the art and is inexpensive to manufacture, since he exists in large numbers and is used for example as a small turbine or as a turbocompressor in cars so far.
- a high-performance compressor in the form of a turbomachine such as a centrifugal compressor can be used, which is well manageable in the art and is inexpensive to manufacture, since he exists in large numbers and is used for example as a small turbine or as a turbocompressor in cars so far.
- a prominent representative of the class of turbomachinery in comparison to displacement machines is the radial compressor, for example in the form of a centrifugal compressor with radial wheel.
- the radial compressor or turbomachine must achieve at least one compression that the outlet pressure from the centrifugal compressor is higher by 5 hPa than the inlet pressure into the centrifugal compressor. Preferably, however, a densification in a ratio greater than 1: 2 and even greater than 1: 3 will be.
- Turbomachines also have the advantage compared to typically used in closed circuits Kolbenverdichtern that the compressor losses due to the existing temperature gradient in the turbomachine compared to a displacement machine (reciprocating compressor), in which such a stationary temperature gradient does not exist, are greatly reduced. It is particularly advantageous that an oil circuit completely eliminated.
- multi-stage turbomachines are particularly preferred in order to achieve the relatively high compression, which, in order to achieve a sufficient flow temperature of a heater for cold winter days, should have a factor of 8 to 10.
- a completely open circuit is used in which groundwater is brought to the low pressure.
- a preferred embodiment for generating a pressure below 20 hPa for groundwater is the simple use of a riser, which in a pressure-tight evaporation chamber opens. If the riser crosses a height between 9 and 10 m, then the required low pressure is present in the evaporation space, at which the groundwater evaporates at a temperature between 7 and 12 ° C.
- the length of the riser can be readily reduced by a pump / turbine combination, due to the fact that the turbine is designed for high to low pressure conversion and the pump for conversion used by the low pressure on the high pressure, only a little extra work needed from the outside.
- no heat exchanger is used in the condenser. Instead, the water vapor heated due to its compression is introduced directly into the heating water in a condenser, so that liquefaction of the water vapor takes place within the water, such that secondary heat exchanger losses are also eliminated.
- the water evaporator fluid machine condenser combination according to the invention thus enables efficiencies of at least factor 6 in comparison to conventional heat pumps.
- This is at least a doubling of efficiency compared to the prior art, or halved compared to energy costs. This applies in particular to climate-relevant emissions of carbon dioxide.
- Fig. 1a shows a heat pump according to the invention, which initially has a water evaporator 10 for evaporating water as a working fluid to the output side to generate a steam in a working steam line 12.
- the evaporator comprises an evaporation space (in Fig. 1a not shown) and is designed to produce an evaporation pressure of less than 20 hPa in the evaporation space, so that the water evaporates at temperatures below 15 ° C in the evaporation space.
- the water is preferably groundwater, in the ground free or in collector pipes circulating brine, so water with a certain salinity, river water, seawater or seawater.
- all types of water ie, calcareous water, lime-free water, saline water, or salt-free water
- all types of water that is, all of these "hydrogens” have the favorable water property, namely that water, also known as "R 718”, is an enthalpy difference ratio useful for the heat pump process of 6 has, which is more than 2 times the typical usable enthalpy difference ratio of z.
- R 718 water
- B. R134a corresponds.
- the water vapor is supplied through the suction line 12 to a compressor / condenser system 14, which is a turbomachine such.
- B. has a centrifugal compressor, for example in the form of a turbocompressor, in Fig. 1a denoted by 16.
- the turbomachine is designed to compress the working steam to a vapor pressure at least greater than 25 hPa.
- 25 hPa corresponds to a liquefaction temperature of about 22 ° C, which can already be a sufficient heating flow temperature of a floor heating, at least on relatively warm days.
- pressures greater than 30 hPa can be generated with the turbomachine 16, wherein a pressure of 30 hPa has a liquefaction temperature of 24 ° C, a pressure of 60 hPa has a liquefaction temperature of 36 ° C, and a pressure of 100 hPa corresponds to a liquefaction temperature of 45 ° C.
- Underfloor heating systems are designed to heat sufficiently with a flow temperature of 45 ° C, even on very cold days.
- the turbomachine is coupled to a condenser 18, which is designed to liquefy the compressed working steam.
- a condenser 18 which is designed to liquefy the compressed working steam.
- the heat (energy) which is taken up by the heating water so that it heats up.
- the steam is so much energy withdrawn that this is liquefied and also participates in the heating circuit.
- a material entry into the condenser or the heating system takes place, which is regulated by a drain 22, such that the condenser has a water level in its condenser, which remains despite the constant supply of water vapor and thus condensate always below a maximum level.
- a heat exchanger can be arranged, which is fed with the flow 20a and having the return 20b, said heat exchanger cools the water in the condenser and thus heats a separate underfloor heating fluid, which will typically be water.
- the turbomachine Due to the fact that water is used as the working medium, and due to the fact that only the evaporated portion of the groundwater is fed into the turbomachine, the purity of the water does not matter.
- the turbomachine, as well as the condenser and possibly directly coupled underfloor heating always supplied with distilled water, so that the system has a reduced maintenance compared to today's systems. In other words, the system is self-cleaning, since the system is always fed only distilled water and the water in the drain 22 is thus not polluted.
- turbomachines have the properties that they - similar to an aircraft turbine - the compressed medium not with problematic substances, such as oil, in connection. Instead, the water vapor is compressed only by the turbine or the turbo compressor, but not associated with oil or other purity-impairing medium and thus contaminated.
- the distilled water discharged through the drain can thus - if no other regulations stand in the way - be easily returned to the groundwater. Alternatively, however, it may also be z. B. in the garden or in an open space to be seeped, or it can be supplied via the channel, if regulations dictate - a sewage treatment plant.
- the water evaporator comprises a vaporization chamber 100 and a riser 102 in which groundwater from a groundwater reservoir 104 moves upwardly in the direction of an arrow 106 into the vaporization space 100.
- the riser 102 opens into an expander 108, which is designed to widen the relatively narrow tube cross-section in order to create the largest possible evaporation surface.
- the expander 108 will be funnel-shaped, that is to say in the form of a paraboloid of revolution of any shape. It can have round or angular transitions.
- the decisive factor is that the diameter directed into the evaporation chamber 100 or the surface facing the evaporation chamber 100 is greater than the cross-sectional area of the riser, in order to improve the evaporation process. If it is assumed that about 1 l per second flows through the riser up into the evaporation chamber, about 4 ml per second are evaporated in the evaporator at a heating power of about 10 kW. The remainder, cooled by about 2.5 ° C, passes over the expander 108 and lands in a collection sump 110 in the vaporization chamber.
- the collecting sump 110 has a drain 112, in which the amount of 1 1 per second less the evaporated 4 ml per second is discharged again, preferably back into the groundwater reservoir 104.
- a pump 114 and a valve for Overflow control provided. It should be noted that nothing has to be pumped actively here, since due to gravity, when the pump or the valve 114 is opened, water flows from the evaporator catch basin 110 via a return pipe 113 down into the groundwater reservoir. The pump or the valve 114 thus ensure that the water level in the catch basin does not rise too high or that no water vapor penetrates into the drain pipe 112 or that the evaporation chamber is reliably decoupled from the situation at the "lower" end of the return pipe 113.
- the riser is arranged in a riser 116, which is filled by a preferably provided pump 118 with water.
- the levels in 116 and 108 are interconnected according to the communicating tube principle, with gravity and the different pressures in 116 and 108 providing water transport from 116 to 108.
- the water level in the riser tank 116 is preferably arranged so that even at different air pressures, the level never falls below the inlet of the riser 102, so that the ingress of air is avoided.
- the evaporator 10 includes a gas separator configured to receive at least a portion, e.g. To remove at least 50% of a gas dissolved in the water to be evaporated, from the water to be evaporated, so that the removed part of the gas is not sucked through the evaporation space of the compressor.
- the gas separator is arranged to a remote part of the gas not supplied evaporated water, so that the gas is transported away from the unevaporated water.
- Dissolved gases may include oxygen, carbon dioxide, nitrogen, etc. These gases usually evaporate at a higher pressure than water so that the gas separator can be arranged below the expander 108, so that oxygen vaporized in the gas separator etc.
- the separated gas can also be collected and disposed of at certain intervals or continuously vented, that is delivered to the atmosphere.
- the groundwater, seawater, river water, seawater, brine or any other naturally occurring aqueous solution will have a temperature between 8 ° C and 12 ° C.
- a power of 4.2 kW can be generated.
- the water is cooled by 2.5 ° C, a power of 10.5 kW is generated.
- the riser is flowed through by a stream of water with a current in dependence on the heating power, in the example one liter per second.
- the evaporator When the heat pump is operating at a relatively high load, the evaporator will vaporize about 6 ml per second, which corresponds to a vapor volume of about 1.2 cubic meters per second.
- the turbomachine is controlled with regard to its compaction performance. If a heating flow temperature of 45 ° C is desired, which is by far sufficient even for extremely cold days, then the turbomachine must increase the steam produced at perhaps 10 hPa to a pressure of 100 hPa. In contrast, a flow temperature of z. B. 25 ° for underfloor heating, so only by a factor of 3 must be compressed by the turbomachine.
- the power generated is therefore determined by the compressor power, so on the one hand by the compression factor, ie how much compressed the compressor, and on the other by the volume flow generated by the compressor.
- the compression factor ie how much compressed the compressor
- the volume flow generated by the compressor As the volumetric flow increases, the evaporator must vaporize more, with the pump 118 conveying more groundwater into the riser basin 116, so that more groundwater is supplied to the vaporization chamber. If, on the other hand, the turbomachine delivers a lower compression factor, less groundwater flows from the bottom to the top.
- the level in the container 116 or the delivery rate of the pump 118 defines the flow through the riser.
- an increase in efficiency of the system can be achieved because the control of the flow is decoupled from the suction power of the turbomachine.
- a pump 152 At the same time the negative pressure on the return side is brought back into the high pressure, the energy required for this is supplied by a pump 152.
- the pump 152 and the turbine 150 are coupled together via a power coupling 154 so that the turbine drives the pump, with the energy that the turbine has removed from the medium.
- a motor 156 is only needed to compensate for the losses that the system has of course, and to achieve the circulation, so as to move a system from its rest position into the in Fig. 5a to bring shown dynamic mode.
- the turbomachine is configured as a rotary compressor with a rotatable wheel, wherein the wheel may be a low-speed radial, medium-radial, semi-axial, or propeller, as known in the art.
- Radial compressors are described in "Turbomachines", C. Pfleiderer, H. Petermann, Springer-Verlag, 2005, pages 82 and 83. Such radial compressors thus include as a rotatable wheel the so-called. Center runner whose form depends on the individual requirements. In general, any flow machines can be used, as they are known as turbo compressors, fans, blowers or turbocompressors.
- the radial compressor 16 is designed as a plurality of independent turbomachines, which can be controlled independently of each other at least in terms of their speed, so that two turbomachines can have different speeds.
- Such an implementation is in Fig. 6a represented, in which the compressor is designed as a cascade of n turbomachines.
- At any point after the first turbomachine one or more heat exchangers, for example, for hot water heating, which are denoted by 170, is preferably provided. These heat exchangers are designed to cool the gas which has been heated (and compressed) by a preceding turbomachine 172.
- the superheat enthalpy is meaningfully used to increase the efficiency of the entire compression process.
- the cooled gas is then further compressed with one or more downstream compressors or fed directly to the condenser. It is removed heat from the compressed water vapor, so that z. As process water to higher temperatures than z. B. 40 ° C to heat. However, this does not reduce the overall efficiency of the heat pump, but even increases it, since two consecutively connected gas cooling turbines with a longer service life achieve the required gas pressure in the condenser due to the reduced thermal stress and less energy than if a single turbomachine without gas cooling would be available.
- the cascaded independently operated turbomachines are preferably controlled by a controller 250, the input side receives a desired temperature in the heating circuit and possibly also an actual temperature in the heating circuit.
- the rotational speed of a turbomachine arranged earlier in the cascade which is denoted by n 1 by way of example, and the rotational speed n 2 of a turbomachine, which is arranged later in the cascade, are changed as indicated by Fig. 6b is shown.
- n 1 by way of example
- n 2 of a turbomachine which is arranged later in the cascade
- Fig. 6b If a higher set temperature is input to the controller 250, both speeds are increased.
- the speed of the previously arranged turbomachine, with n 1 in Fig. 6b is increased with a smaller gradient than the rotational speed n 2 of a later arranged in the cascade turbo machine.
- the graph of Fig. 6b gives a straight line with a positive slope.
- intersection between the individually applied rotational speeds n 1 and n 2 can take place at any desired point, that is to say at any desired temperature and, if appropriate, can not take place. In general, however, it is preferable to lift a turbomachine arranged closer to the condenser in the cascade more strongly in terms of its rotational speed than a turbomachine arranged earlier in the cascade, if a higher desired temperature is desired.
- a turbomachine arranged more in the cascade in the direction of the condenser has a direction of rotation of the radial wheel which is opposite to the direction of rotation of a radial wheel previously arranged in the cascade.
- a nearly optimal entry angle of the blades of both axial wheels can be achieved in the gas flow, such that a favorable efficiency of the turbomachine cascade occurs not only in a small target temperature range, but in a much larger target temperature range between 20 and 50 degrees, which is an optimal range for typical heating applications.
- the speed control according to the invention and, where appropriate, the use of counter-rotating axial gears thus provides an optimal match between the variable gas flow with changing target temperature on the one hand and the fixed blade angles of the axial wheels on the other.
- At least one or preferably all of the axial gears of all flow machines are made of plastic having a tensile strength above 80 MPa.
- a preferred plastic this is polyamide 6.6 with inserted carbon fibers. This plastic has the advantage of tensile strength, so that Axialzier the fault machines can be made of this plastic and yet can be operated at high speeds.
- Axial wheels are preferably used according to the invention, as for example in Fig. 6c at reference numeral 260.
- Fig. 6c shows a schematic plan view of such a radial wheel, wherein Fig. 6d a schematic cross-sectional view of such a radial wheel shows.
- a radial wheel as known in the art, includes a plurality of inwardly outwardly extending vanes 262. The vanes extend from a distance of a central axis 264, designated r w , entirely outward with respect to the axis 264 of the radial wheel.
- the radial wheel comprises a base 266 and a lid 268 which is directed to the intake manifold or to an earlier stage compressor.
- the radial wheel comprises a suction port, designated r 1 , for sucking gas, which gas is then discharged laterally from the radial wheel, as indicated at 270 in FIG Fig. 6d is specified.
- blades 272, 274 and 276, respectively which are less long than the blade 262 extend.
- the vanes 272 do not extend from r w to the outside, but outwardly from R 1 with respect to the radial wheel, where R 1 is greater than r w .
- the vanes 274 extend outwardly from R 2 only, while the vanes 276 extend outwardly only from R 3 , where R 2 is greater than R 1 and R 3 is greater than R 2 .
- Fig. 6d shown schematically, with a double hatching, for example in the area 278 in Fig. 6d indicates that there are two blades in this area that overlap and are therefore marked by the double-hatched area.
- the hatching from bottom left to top right in the area 278 denotes a vane 262 w extends from r to by the very outside, while extending from top left to bottom right of the area 278 hatching indicates a vane 272 which merely to extends from R 1 to the outside with respect to the radial wheel.
- At least one blade which does not extend so far inwardly, is thus arranged between two blades extending deeper inwardly.
- the intake is not clogged or areas with a smaller radius are not too heavily occupied with blades, while areas with a larger radius are more densely occupied with blades, so that at the exit of the radial wheel, ie where the compressed gas Radial wheel leaves, as homogeneous a velocity distribution of the exiting gas exists.
- the velocity distribution of the exiting gas is in the preferred radial wheel according to the invention in Fig.
- the relatively complex and complicated shape of the radial wheel in Fig. 6c Particularly favorable can be produced with plastic injection molding, which in particular can be easily achieved that all blades, including the blades that do not extend from the very inside to the very outside, so the blades 272, 274, 276 are firmly anchored, as they both with the lid 268 so on the basis 266 of Fig. 6d are connected.
- plastic injection molding which in particular can be easily achieved that all blades, including the blades that do not extend from the very inside to the very outside, so the blades 272, 274, 276 are firmly anchored, as they both with the lid 268 so on the basis 266 of Fig. 6d are connected.
- the use of plastic in particular with the plastic injection molding technology makes it possible to produce any shapes accurately and inexpensively, which is not readily possible with axial wheels made of metal or only very expensive or possibly even impossible.
- plastic is also favorable due to the superior impact resistance of plastic. So it is not always ruled out that ice crystals or water droplets hit the radial wheel at least the first compressor stage. Due to the high accelerations, very high impact forces arise here, which are easily withstood by plastics with sufficient impact resistance. Furthermore, the liquefaction in the liquefier preferably takes place on the basis of the cavitation principle. Here steam bubbles fall due to this principle in a volume of water in itself. There are also microscopically quite considerable velocities and forces arising over the long term Seen view can lead to material fatigue, which, however, when a plastic is used with a sufficient impact resistance, are easily manageable.
- the compressed gas discharged from the last compressor 174 that is, the compressed steam, is then supplied to the condenser 18, which may be configured as shown in FIG Fig. 2 is shown, but which is preferably designed as in Fig. 3a is shown.
- the condenser 18 contains a volume of water 180, and preferably an arbitrarily small volume of steam 182.
- the condenser 18 is designed to feed the compressed vapor into the water of the volume of water 180, so that where the vapor enters the liquid immediately results in condensation as schematically indicated at 184.
- the gas supply has a widening region 186, such that the gas is distributed as extensively as possible in the condenser water volume 180.
- the heating flow is placed as close as possible to the surface of the water volume 180 to always remove the warmest water from the condenser water volume 180.
- the heating return is fed down the condenser, so that the steam to be liquefied always comes in contact with the coolest possible water, which due to the circulation using a heating circulation pump 312 again from below towards the steam-water boundary of the expander 186 moves.
- Fig. 5b shows an implementation of a connection of a heating line to the condenser with a turbine / pump combination, if the condenser is to be located at a lower height than the heating line, or if a conventional heater, which requires a higher pressure, to be connected.
- the pump 312 is designed as a driven pump, as at 312 in FIG Fig. 5b is shown.
- a turbine 310 is provided in the heater return 20b for driving the pump 312, which is connected via a power coupling 314 to the pump 312. The high pressure then prevails in the heater and the low pressure prevails in the condenser.
- the drain 22 is provided above which, so that the water level in the condenser does not change substantially, also z. B. have to drain about 4 ml per second.
- a drain pump or a drain valve 192 is provided for pressure control, such that without pressure loss, the required amount of z. B. 4 ml per second, ie the amount that is supplied to the steam liquefier with the compressor running, is discharged again.
- the drain may be introduced into the riser, as shown at 194.
- the return 112 from the evaporator can be fed without problems into the groundwater, since the water returning there was in contact only with the riser and the return line, but did not exceed the "evaporation limit" between the evaporator expander 108 and the outlet to the turbomachine Has.
- Fig. 3a represents a preferred embodiment for the condenser 18.
- the compressed steam supply line 198 is placed in the condenser so that the steam just below the surface of the condenser water volume 180 can escape into this volume of water.
- the end of the steam supply line around the circumference of the tube arranged around nozzles, through which the steam can escape into the water.
- an expander 200 is provided. This expansion is located in the condenser water volume 180.
- a circulating pump 202 which is adapted to suck cold water at the bottom of the condenser and through the expander in to shift an upward broadening flow. This is intended to bring as large amounts of the entering into the condenser water 180 steam with cold water as possible, which is supplied by the circulation pump 202 in combination.
- a sound insulation 208 which may be active or passive. Passive sound insulation, like thermal insulation, will insulate the frequencies of the sound produced by the liquefaction process as well as possible. Likewise, it is also preferred to silencing the other components of the system.
- the sound insulation may alternatively be actively formed, in which case z. B. would have a microphone for sound measurement and in response would trigger a sound-counteraction, such as an in-vibration displacement of an outer condenser wall, etc. with z. B. piezoelectric means.
- a return valve may be disposed in line 198, eg, near the exit of the line from the condenser.
- line 198 may be led up to the point where no liquid is returned to the compressor when the compressor is turned off.
- the condenser comprises a nozzle plate 210 which has nozzles 212 protruding with respect to the plane of the nozzle plate 210.
- the nozzles 212 extend below the water level of the water volume 180 in the condenser.
- the nozzle 212 has nozzle openings through which the compressed vapor that propagates from the conduit 198 within the vapor volume 182 may enter the condenser water, as shown schematically by arrows 216.
- the warm water then either enters immediately into the feed 20a or spreads over the Aufweiter edge in the water volume, as shown by an arrow 218, so that in the condenser outside the Aufweiters a temperature stratification occurs, which is disturbed as little as possible, in particular due to the expander shape.
- the flow velocity at the edge of the expander is substantially lower than in the middle. It is preferred to operate the condenser as a temperature-layer storage such that the heat pump, and in particular the compressor, does not have to run continuously, but only has to run when needed, as is the case for normal heating systems, e.g. working with an oil burner is also the case.
- Fig. 3c shows a further preferred implementation of the condenser in a schematic form.
- the condenser comprises a gas separator 220, which is coupled to the gas volume 182 in the condenser.
- Gas generated in the condenser such as oxygen or another gas which may outgas in the condenser, accumulates in the gas separator vessel 220.
- This gas can then be pumped to the atmosphere by operating a pump 222, preferably at certain intervals, since continuous gas pumping is not necessary due to the small amount of gas produced.
- the gas can also be returned to the return 112 or 113 of Fig. 2 be docked, so that the gas is brought back together with the returning groundwater back into the groundwater reservoir, where it is then dissolved in the groundwater again, or when it enters the groundwater reservoir, there goes into the atmosphere.
- the system of the invention works with water, even with strong outgassing no gases that were not previously solved in the groundwater, so that the separated gas has no environmental problems in itself.
- the system according to the invention has at each point as a working medium water or Steam which is at least as clean as the original groundwater, or even cleaner than the groundwater due to evaporation in the evaporator, since it is distilled water when the compressed steam in the condenser has been re-liquefied.
- Fig. 4a a preferred embodiment of the evaporator shown in order to use the condenser flow advantageously for accelerating the evaporation process.
- the process which is yes to heating return temperature, that is, a much higher temperature than the groundwater funded from the ground, passed through the expander 108 of the evaporator, so that the wall of the drain pipe 204 as a germ for a Bubble boiling acts.
- heating return temperature that is, a much higher temperature than the groundwater funded from the ground
- the expander 108 of the evaporator passed through the expander 108 of the evaporator, so that the wall of the drain pipe 204 as a germ for a Bubble boiling acts.
- This is much more efficient steam generated by the evaporator than if no such germination is provided.
- a region of the evaporator on which water to be evaporated is located may be made of a rough material in order to supply nuclei for nucleate boiling.
- a rough grid can be arranged below the water surface of the water to be evaporated.
- Fig. 4b shows an alternative implementation of the evaporator.
- the condenser outlet 22 of Fig. 2 optionally via a pump 192 or, if circumstances permit, without a pump, connected to a nozzle tube 230 having a termination 232 at one end and nozzle orifices 234.
- the warm condenser water which is discharged from the condenser via the drain 22 at a rate of, for example, 4 ml per second, is now fed to the evaporator. It will evaporate on its way to a nozzle opening 234 in the nozzle tube 230 or directly at the outlet to a nozzle due to the low pressure for the temperature of the drain water to a certain extent below the water surface of the evaporator water.
- the resulting vapor bubbles are directly as boiling nuclei for the evaporator water, which is conveyed via the inlet 102, act. This can be triggered without major additional measures efficient bubble boiling in the evaporator, this triggering similar to Fig. 4a due to the fact that the temperature near the rough region 206 in Fig. 4a or in the vicinity of a nozzle opening 234 is already so high that immediately takes place at the present pressure evaporation.
- This evaporation forces the generation of a vapor bubble which, if the conditions are favorably chosen, has a very high probability that it will not collapse again, but that it will develop into a surface-going vapor bubble which, as soon as it enters the Steam volume has entered the evaporation chamber, is sucked through the suction pipe 12 from the compressor.
- Fig. 4c shown embodiment can be used.
- the warm condenser water supplied from the condenser outlet 22 is introduced, for example, at a rate of 4 ml per second into a heat exchanger 236 to deliver its heat to a groundwater coming from the main groundwater flow in the line 102 via a branch line 238 and a branch pump 240 has been branched off.
- the branched groundwater then substantially decreases the heat of the condenser outlet within the heat exchanger 236, so that preheated groundwater, for example, at a temperature of 33 ° C is introduced into the nozzle tube 230, by the high compared to the groundwater temperature, the nucleate in Effectively trigger or support evaporators.
- the heat exchanger via a drain line 238 relatively strongly cooled drain water, which is then fed via a drain pump 240 of the sewer. Due to the combination of branch line 238 and branch pump 240 and heat exchanger 236 only groundwater is used in the evaporator or introduced without it was in contact with another medium. A relevance in terms of water law thus exists in the Fig. 4c not shown embodiment.
- Fig. 4d shows an alternative implementation of the evaporator with edge feed.
- the expander 200 of the evaporator located below the water level 110 in the evaporator.
- water flows "from the outside" into the center of the expander and is then returned to a central conduit 112.
- the center line in Fig. 2 has served to feed the evaporator, it serves in Fig. 4d now for deriving the unevaporated groundwater.
- the in Fig. 2 shown line 112 for the removal of unevaporated groundwater served.
- this line on the edge acts as a groundwater supply.
- Fig. 4e shows a preferred implementation of Aufweiters 200, as it can be used in the evaporator, or the expander, as it can be used for example in the condenser, and as it is for example in Fig. 2 or Fig. 3a or 3b is shown.
- the expander is preferably designed so that its small diameter preferably enters the expander at the center of the "large" expander surface. This diameter of this inlet or outlet (in Fig. 4d ) is preferably between 3 and 10 cm and in particularly preferred embodiments between 4 and 6 cm.
- the large diameter d 2 of the expander is in preferred embodiments between 15 and 100 cm and is smaller than 25 cm in particularly preferred embodiments.
- the small version of the evaporator is possible when efficient measures for triggering and supporting the bubble boiling are used, as explained above.
- a curvature region of the expander which is preferably designed to give a laminar flow in this region which is of a fast flow rate, preferably in the range of 7 to 40 cm per second, is lowered to a relatively small flow rate at the edge of the expander. Strong flow rate discontinuities, such as vortices in the area of the line of curvature or "bubbling effects" above the inlet when viewed from the top of the expander, are preferably avoided as they may be detrimental to efficiency.
- the expander has a shape which causes the height of the water level above the expander surface to be less than 15 mm and preferably between 1 and 5 mm. It is therefore preferred to use an expander 200 which is designed such that in more than 50% of the area of the expander, when viewed from above, there is a water level which is smaller than 15 mm. This ensures efficient evaporation over the entire area, which is particularly enhanced in terms of efficiency when using measures to trigger bubble boiling.
- the heat pump according to the invention thus serves for efficient heat supply of buildings and no longer requires working equipment that has a global climate-damaging influence.
- water is evaporated under very low pressure, compressed by one or more turbomachines arranged one behind the other and liquefied again into water.
- the transporting energy is used for heating.
- a heat pump is used, which is preferably an open system. Open system here means that groundwater or other available thermal energy-carrying aqueous medium is evaporated, compacted and liquefied under low pressure.
- the water is used directly as a working medium.
- the contained energy is therefore not transferred to a closed system.
- the liquefied water is preferably used directly in the heating system and then fed back to the groundwater. To decouple the heating system capacitively, it can also be completed via a heat exchanger.
- the eighth comes from the fact that only in the most extreme cold a sixth must be spent, and z. B. at transition temperatures such as in March or the end of October, the efficiency can rise to a value greater than 12, so that a maximum of one-eighth must be spent on average over the year.
- the housing of the evaporator, the compressor and / or the condenser and also especially the radial impeller of the fluid machine made of plastic and in particular of injection-molded plastic In order to reduce the manufacturing costs and also to reduce the maintenance and assembly costs, it is preferable to carry out the housing of the evaporator, the compressor and / or the condenser and also especially the radial impeller of the fluid machine made of plastic and in particular of injection-molded plastic.
- Plastic is well suited, since plastic is corrosion-resistant with respect to water and, according to the invention, advantageously the maximum temperatures are significantly below the deformation temperatures of usable plastics in comparison with conventional heaters.
- the assembly is particularly simple, since there is negative pressure in the system of evaporator, compressor and condenser. As a result, the requirements for the gaskets are significantly reduced because the entire atmospheric pressure helps to keep the housings tight.
- Plastic is also particularly well, since at no point high temperatures occur in the system according to the invention, which would require the use of expensive special plastics, metal or ceramic.
- plastic injection molding and the shape of the radial wheel can be arbitrarily optimized and yet easily and inexpensively manufactured in spite of complicated shape.
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Abstract
Description
Die vorliegende Erfindung bezieht sich auf Wärmepumpen und insbesondere auf Wärmepumpen, die zur Gebäudeheizung und speziell zur Gebäudeheizung von kleineren Gebäudeeinheiten, wie beispielsweise Einfamilienhäusern, Doppelhäusern oder-Reihenhäusern eingesetzt werden können.The present invention relates to heat pumps and more particularly to heat pumps that can be used for building heating and especially for heating buildings of smaller building units, such as single-family homes, semi-detached houses or terraced houses.
Wie hieraus ersichtlich ist, dient das Arbeitsmittel als Energietransporteur um aus dem Erdreich bzw. Grundwasser Wärme aufzunehmen und diese im Verflüssiger an den Heizungskreislauf abzugeben. Bei dieser Prozessführung ist der 2. Hauptsatz der Thermodynamik erfüllt, in dem es heißt, dass Wärme bzw. Energie von "selbst" nur vom höheren Temperaturniveau auf das niedrigere Temperaturniveau übertragen werden kann, und dass dies umgekehrt nur durch äußere Energiezufuhr, hier die Antriebsarbeit des Verdichters, geschehen kann.As can be seen from this, the working medium serves as an energy transporter to pick up heat from the ground or groundwater and deliver it to the heating circuit in the condenser. In this litigation, the second law is the Thermodynamics fulfilled, in which it is said that heat or energy from "self" can only be transferred from the higher temperature level to the lower temperature level, and that conversely this can only happen by external energy supply, here the drive work of the compressor.
Zwischen Punkt 1 und Punkt 2 findet idealerweise eine reversible Verdichtung des Arbeitsmitteldampfes in einem adiabaten Verdichter auf den Druck p2 statt. Dabei steigt die Temperatur auf T2. Es ist hier eine Verdichtungsarbeit zuzuführen.Between
Dann wird bei hohem Druck p2 zunächst eine isobare Kühlung des Arbeitsmitteldampfes von 2 auf 2' durchgeführt. Die Überhitzung wird abgebaut. Anschließend findet eine Verflüssigung des Arbeitsmittels statt. Insgesamt kann die Wärme Q25 abgeführt werden.Then, at high pressure p 2 , an isobaric cooling of the working medium vapor is first carried out from 2 to 2 '. The overheating is reduced. Subsequently, a liquefaction of the working fluid takes place. Overall, the heat Q 25 can be dissipated.
In der Drossel 83 findet dann die adiabate Drosselung des Arbeitsmittels vom hohen Druck p2 auf den niedrigen Druck p1 statt. Dabei verdampft ein Teil des flüssigen Arbeitsmittels und die Temperatur verringert sich auf die Verdampfungstemperatur T1. In dem h, log p-Diagramm können die Energien und Kennzahlen dieses Prozesses mittels Enthalpien berechnet werden und veranschaulicht werden, wie es in
Das Arbeitsfluid der Wärmepumpe nimmt somit im Verdampfer Wärme aus der Umgebung, d. h. Luft, Wasser, Abwasser oder Erdboden, auf. Der Verflüssiger dient als Wärmeübertrager zum Erwärmen eines Heizmittels. Die Temperatur T1 liegt etwas unter der Umgebungstemperatur die Temperatur T2 erheblich, die Temperatur T2' etwas über der benötigten Heizungstemperatur. Je höher die geforderte Temperaturdifferenz ist, umso mehr Arbeit muss der Verdichter aufbringen. Man ist daher bestrebt, die Temperaturerhöhung so klein wie möglich zu halten.The working fluid of the heat pump thus takes in the evaporator heat from the environment, ie air, water, sewage or soil, on. The condenser serves as a heat exchanger for heating a heating medium. The temperature T 1 is slightly below the ambient temperature, the temperature T 2 considerably, the temperature T 2 'slightly above the required heating temperature. The higher the required temperature difference, the more work the compressor must apply. It is therefore desirable to keep the temperature increase as small as possible.
Bezugnehmend auf
Bei Kolben-Verdichtern hat der angesaugte Arbeitsstoffdampf zunächst eine niedrigere Temperatur als die Zylinderwandung des Verdichters und nimmt Wärme aus ihr auf. Mit fortschreitender Verdichtung erhöht sich schließlich die Temperatur des Arbeitsstoffdampfes über die der Zylinderwandung, so dass der Arbeitsstoffdampf Wärme an die Zylinderwandung abgibt. Dann, wenn der Kolben erneut Dampf ansaugt und verdichtet, wird die Temperatur der Kolbenwandung zunächst wieder unterschritten und dann überschritten, was zu dauernden Verlusten führt. Ferner wird eine Überhitzung des angesaugten Arbeitsstoffdampfes nötig und erforderlich sein, damit der Verdichter keinen flüssigen Arbeitsstoff ansaugt. Nachteilig ist insbesondere auch der Wärmeaustausch mit dem Ölkreislauf des Kolbenverdichters, welcher zur Schmierung unverzichtbar ist.In piston compressors, the aspirated working vapor initially has a lower temperature than the cylinder wall of the compressor and absorbs heat from it. As the compression progresses, the temperature of the working-material vapor finally increases above that of the cylinder wall, so that the working-substance vapor gives off heat to the cylinder wall. Then, when the piston again sucks in steam and compressed, the temperature of the piston wall is initially again fallen below and then exceeded, resulting in permanent losses. Furthermore, overheating of the aspirated working fluid will be necessary and necessary so that the compressor does not suck liquid agent. A disadvantage is in particular the heat exchange with the oil circuit of the reciprocating compressor, which is indispensable for lubrication.
Auftretende Irreversibilitäten, wie Wärmeverluste bei der Verdichtung, Druckverluste in den Ventilen und Strömungsverluste in der Druckleitung zum Verflüssigen und in dem Verflüssiger erhöhen die Entropie, also die Wärme, die nicht mehr wiedergewonnen werden kann. Ferner liegt auch die Temperatur T2 über der Verflüssigungstemperatur. Eine solche "Überhitzungsenthalpie" ist unerwünscht, besonders, weil die dabei auftretenden hohen Temperaturen die Alterung des Verdichters und insbesondere des Schmieröls bei einem Kolben-Verdichter beschleunigen. Auch wird die Effektivität des Prozesses gemindert.Occurring irreversibilities, such as heat losses during compression, pressure losses in the valves and flow losses in the pressure line for liquefying and in the condenser increase the entropy, ie the heat that can not be recovered. Furthermore, the temperature T 2 is also above the liquefaction temperature. Such an "overheating enthalpy" is undesirable, especially because the high temperatures occurring accelerate the aging of the compressor and in particular of the lubricating oil in a piston compressor. Also, the effectiveness of the process is reduced.
Der verflüssigte Arbeitsstoff auf niedriger Temperatur am Ausgang des Verflüssigers müsste im Rahmen eines idealen Kreisprozesses über eine Kraftmaschine, beispielsweise Turbine, entspannt werden, um den Überschuss an Energie, der gegenüber dem Zustand bei der Temperatur und dem Druck vor dem Verdichten bestand, zu nützen. Aus Gründen des hierfür erforderlichen großen Aufwands unterbleibt diese Maßnahme und der Druck des Arbeitsstoffes wird durch die Drossel 83 schlagartig auf den niedrigen Druck und die niedrige Temperatur herabgesetzt. Die Enthalpie des Arbeitsstoffes bleibt hierbei angenähert gleich. Durch die schlagartige Druckminderung muss der Arbeitsstoff teilweise verdampfen, um seine Temperatur abzusenken. Die notwendige Verdampfungswärme stammt aus dem auf Übertemperatur befindlichen Arbeitsstoff, wird also nicht der Wärmequelle entzogen. Die Gesamtheit der durch die Entspannung in der Drossel 83 (
Ein derzeit populäres Arbeitsmittel ist R134a, das als chemische Formel CF3-CH2F hat. Hier handelt es sich um ein Arbeitsmittel, das zwar nicht mehr ozonschädigend ist, das jedoch im Hinblick auf den Treibhauseffekt eine 1000 mal stärkere Wirkung als Kohlendioxid hat. Das Arbeitsmittel R134a wird jedoch gerne verwendet, da es eine relativ große Enthalpie-Differenz von etwa 150 kJ/kg hat.A currently popular tool is R134a, which has CF 3 -CH 2 F as its chemical formula. This is a working fluid that is no longer harmful to the ozone layer, but has a 1000 times greater effect than carbon dioxide in terms of the greenhouse effect. However, the working fluid R134a is popular because it has a relatively large enthalpy difference of about 150 kJ / kg.
Obgleich dieses Arbeitsmittel kein "Ozonkiller" mehr ist, existieren dennoch erhebliche Anforderungen an die Geschlossenheit des Wärmepumpen-Kreislaufs, derart, dass aus diesem geschlossenen Kreislauf keine Arbeitsmittel-Moleküle austreten, da diese ganz erhebliche Schäden aufgrund des Treibhauseffekts anrichten würden. Diese Kapselung verursacht erhebliche Zusatzkosten beim Bau einer Wärmepumpe.Although this working fluid is no longer an "ozone killer", there are still considerable demands on the integrity of the heat pump cycle, such that no working fluid molecules escape from this closed circuit, since these would cause quite considerable damage due to the greenhouse effect. This encapsulation causes significant additional costs when building a heat pump.
Ferner ist davon auszugehen, dass bis zur Umsetzung der nächsten Stufe des Kyoto-Protokolls aufgrund des Treibhaus-Effekts bis zum Jahre 2015 auch R134a verboten wird, was auch schon früheren mit wesentlich schädlicheren Mitteln geschehen ist.It is also expected that until the implementation of the next stage of the Kyoto Protocol due to the greenhouse effect, R134a will be banned until 2015, which has been done earlier with much more harmful means.
Nachteilig an bestehenden Wärmepumpen ist daher neben der Tatsache des schädlichen Arbeitsmittels auch die Tatsache, dass aufgrund der vielen Verluste im Wärmepumpenkreislauf der Wirkungsgrad der Wärmepumpe typischerweise nicht über einen Faktor 3 liegt. Anders ausgedrückt, kann man etwa das 2-fache der Energie, die für den Verdichter eingesetzt worden ist, aus der Wärmequelle, wie beispielsweise dem Grundwasser oder dem Erdreich entnehmen. Wenn man nunmehr Wärmepumpen betrachtet, bei denen der Verdichter mit elektrischem Strom angetrieben wird, und wenn man gleichzeitig berücksichtigt, dass der Wirkungsgrad bei der Stromerzeugung vielleicht gleich 40 % ist, so stellt sich heraus, dass - im Hinblick auf die gesamte Energiebilanz - eine Wärmepumpe vom Nutzen her zweifelhaft ist. Bezogen auf den Primärenergieträger werden 120 % = 3 40 % an Heizenergie bereit gestellt. Eine konventionelle Heizanlage mit einem Brenner kommt immerhin auf Wirkungsgrade von 90 - 95 %, d.h. mit einem hohen technischen und damit finanziellen Aufwand wird lediglich eine Verbesserung von 25 - 30 % erreicht.A disadvantage of existing heat pumps is therefore in addition to the fact of the harmful working fluid and the fact that due to the many losses in the heat pump cycle, the efficiency of the heat pump is typically not more than a factor of 3. In other words, about 2 times the energy used for the compressor can be taken from the heat source, such as groundwater or soil. Considering now heat pumps in which the compressor is driven by electric current, and at the same time taking into account that the efficiency in power generation is perhaps equal to 40%, so turns out that - in terms of the overall energy balance - a heat pump is doubtful in terms of utility. Based on the primary energy source, 120% = 3 40% of heating energy is provided. After all, a conventional heating system with a burner achieves efficiencies of 90 - 95%, ie with a high technical and thus financial expense only an improvement of 25 - 30% is achieved.
Bessere Systeme verwenden zum Antrieb des Verdichters Primärenergie. Es wird also Gas oder Öl verbrannt, um mit der durch die Verbrennung frei werdenden Energie die Verdichterleistung zu schaffen. Vorteilhaft an dieser Lösung ist, dass die Energiebilanz tatsächlich positiver wird. Dies hat als Grund, dass als Antriebsenergie zwar lediglich ca. nur 30 % des Primärenergieträgers gewonnen werden können, aber dafür die Abwärme von dann ca. 70 % mit zur Heizung herangezogen werden kann. Die bereitgestellte Heizenergie beträgt dann 160 % = 3 30 % + 70 % des Primärenergieträgers. Nachteilhaft an dieser Lösung ist jedoch, dass, ein Haushalt, obgleich er keine klassische Heizung mehr hat, dennoch einen Verbrennungsmotor und ein Treibstofflager benötigt. Der Aufwand für Motor und Treibstofflager kommen noch zum Aufwand für die Wärmepumpe hinzu, die ja ein hoch-geschlossener Kreislauf aufgrund des klimaschädigenden Kühlmittels ist.Better systems use primary energy to drive the compressor. So gas or oil is burned to create the compressor power with the energy released by the combustion. An advantage of this solution is that the energy balance is actually more positive. This has as a reason that only about 30% of the primary energy carrier can be obtained as drive energy, but for the waste heat of then about 70% can be used for heating. The heating energy provided is then 160% = 3 30% + 70% of the primary energy source. A disadvantage of this solution, however, is that, a household, although he has no more classical heating, still requires an internal combustion engine and a fuel storage. The cost of engine and fuel storage are still added to the cost of the heat pump, which is a high-closed circuit due to the climate-damaging coolant.
Alle diese Dinge haben dazu geführt, dass sich Wärmepumpen in der Konkurrenz zu anderen Heizungsarten nur bedingt behaupten können.All of these things have meant that heat pumps can only compete to a certain extent in competition with other types of heating.
Die
Die
Das
Die
Die Aufgabe der vorliegenden Erfindung besteht darin, ein effizienteres Wärmepumpenkonzept zu schaffen.The object of the present invention is to provide a more efficient heat pump concept.
Diese Aufgabe wird durch eine Wärmepumpe gemäß Patentanspruch 1, oder ein Verfahren zum Pumpen von Wärme gemäß Patentanspruch 9 gelöst.This object is achieved by a heat pump according to
Der vorliegenden Erfindung liegt die Erkenntnis zugrunde, dass von klimaschädigenden Arbeitsmitteln weggegangen werden muss, und dass statt dessen normales Wasser ein optimales Arbeitsmittel ist. Im Vergleich zu dem derzeit häufig verwendeten Arbeitsmittel R134a hat Wasser zudem ein wesentlich größeres Verhältnis der Enthalpie-Differenzen. Die Enthalpie-Differenz, die dafür entscheidend ist, wie groß die Effektivität des Wärmepumpen-Prozesses ist, beträgt bei Wasser etwa 2500 kJ/kg, was etwa 16 mal so groß ist wie die nutzbare Enthalpie-Differenz von R134a. Die aufzuwendende Verdichter-Enthalpie ist dagegen nur 4 - 6 mal so groß, je nach Arbeitspunkt.The present invention is based on the recognition that it is necessary to move away from climate-damaging working materials, and that instead normal water is an optimal working medium. In addition, water has a much larger ratio of enthalpy differences than the currently widely used R134a. The enthalpy difference, which is crucial to the effectiveness of the heat pump process, is about 2500 kJ / kg for water, which is about 16 times the useful enthalpy difference of R134a. By contrast, the compressor enthalpy to be used is only 4 to 6 times greater, depending on the operating point.
Darüber hinaus ist Wasser nicht klimaschädigend, also weder ein Ozonkiller noch ein Treibhauseffekt-Verschärfer. Dies ermöglicht es, dass Wärmepumpen erheblich einfacher gebaut werden können, da die Anforderungen an die Geschlossenheit des Kreislaufs nicht hoch sind. Statt dessen wird es sogar bevorzugt, von dem geschlossenen Prozess ganz wegzugehen und statt dessen einen offenen Prozess zu machen, bei dem das Grundwasser bzw. das Wasser, das die äußere Wärmequelle darstellt, direkt verdampft wird.In addition, water is not climate damaging, so neither an ozone killer nor a greenhouse effect intensifier. This allows heat pumps to be made much simpler, since the demands on the integrity of the circuit are not high. Instead, it is even preferred to go completely away from the closed process and instead to make an open process in which the groundwater or water, which is the external heat source, is directly evaporated.
Erfindungsgemäß ist der Verdampfer derart ausgebildet, dass er einen Verdampfungsraum aufweist, in dem der Verdampfungsdruck kleiner als 20 hPa (Hektopascal) ist, so dass das Wasser bei Temperaturen unter 18°C und vorzugsweise unter 15°C verdampft. Typisches Grundwasser hat in der nördlichen Hemisphäre Temperaturen zwischen 8 und 12°C, was Drücke von unter 20 hPa erfordert, damit das Grundwasser verdampft, um durch das Grundwasserverdampfen eine Absenkung der Temperatur des Grundwassers und damit einen Wärmeentzug erreichen zu können, durch den eine Gebäudeheizung, wie beispielsweise eine Fußbodenheizung betrieben werden kann.According to the invention, the evaporator is designed such that it has an evaporation space in which the evaporation pressure is less than 20 hPa (hectopascal), so that the water evaporates at temperatures below 18 ° C and preferably below 15 ° C. Typical groundwater has temperatures in the northern hemisphere between 8 and 12 ° C, which requires pressures of less than 20 hPa, so that the groundwater evaporates in order to be able to achieve a lowering of the temperature of the groundwater and thus a heat extraction by the groundwater evaporation a building heating, such as a floor heating can be operated.
Wasser ist ferner dahingehend von Vorteil, dass Wasserdampf ein sehr großes Volumen einnimmt, und dass damit zum Verdich ten des Wasserdampfes nicht mehr auf eine Verdrängungsmaschine wie eine Kolbenpumpe oder etwas ähnliches zurückgegriffen werden muss, sondern ein Hochleistungsverdichter in Form einer Strömungsmaschine wie eines Radialverdichters eingesetzt werden kann, der in der Technik gut beherrschbar ist und im Hinblick auf seine Herstellung preisgünstig ist, da er in hohen Stückzahlen existiert und beispielsweise als Kleinturbine oder als Turboverdichter in Autos bisher eingesetzt wird.Water is further advantageous in that water vapor occupies a very large volume, and thus to the compaction ten of the steam no longer on a displacement machine such as a piston pump or something similar must be resorted to, but a high-performance compressor in the form of a turbomachine such as a centrifugal compressor can be used, which is well manageable in the art and is inexpensive to manufacture, since he exists in large numbers and is used for example as a small turbine or as a turbocompressor in cars so far.
Ein prominenter Vertreter der Klasse von Strömungsmaschinen im Vergleich zu Verdrängungsmaschinen ist der Radialverdichter beispielsweise in Form eines Turboverdichters mit Radialrad.A prominent representative of the class of turbomachinery in comparison to displacement machines is the radial compressor, for example in the form of a centrifugal compressor with radial wheel.
Der Radialverdichter bzw. die Strömungsmaschine muss wenigstens eine Verdichtung erreichen, dass der Ausgangsdruck aus dem Radialverdichter um 5 hPa höher als der Eingangsdruck in den Radialverdichter ist. Vorzugsweise wird jedoch eine Verdichtung in einem Verhältnis größer als 1:2 und sogar größer als 1:3 sein.The radial compressor or turbomachine must achieve at least one compression that the outlet pressure from the centrifugal compressor is higher by 5 hPa than the inlet pressure into the centrifugal compressor. Preferably, however, a densification in a ratio greater than 1: 2 and even greater than 1: 3 will be.
Strömungsmaschinen haben ferner im Vergleich zu typischerweise in geschlossenen Kreisläufen verwendeten Kölbenverdichtern den Vorteil, dass die Verdichter-Verluste aufgrund des bestehenden Temperaturgradienten in der Strömungsmaschine im Vergleich zu einer Verdrängungsmaschine (Kolbenverdichter), bei der ein solcher stehender Temperaturgradient nicht existiert, stark reduziert sind. Besonders vorteilhaft ist, dass ein Ölkreislauf komplett entfällt.Turbomachines also have the advantage compared to typically used in closed circuits Kolbenverdichtern that the compressor losses due to the existing temperature gradient in the turbomachine compared to a displacement machine (reciprocating compressor), in which such a stationary temperature gradient does not exist, are greatly reduced. It is particularly advantageous that an oil circuit completely eliminated.
Ferner werden mehrstufige Strömungsmaschinen besonders bevorzugt, um die relativ hohe Verdichtung zu erreichen, die, um auch für kalte Wintertage eine ausreichende Vorlauftemperatur einer Heizung zu erreichen, den Faktor 8 bis 10 haben sollte.Furthermore, multi-stage turbomachines are particularly preferred in order to achieve the relatively high compression, which, in order to achieve a sufficient flow temperature of a heater for cold winter days, should have a factor of 8 to 10.
Bei einem bevorzugten Ausführungsbeispiel wird ein komplett offener Kreislauf eingesetzt, in dem Grundwasser auf den niedrigen Druck gebracht wird. Ein bevorzugtes Ausführungsbeispiel zum Erzeugen eines Drucks unter 20 hPa für Grundwasser besteht in der einfachen Verwendung eines Steigrohrs, das in einen druckdichten Verdampfungsraum mündet. Überwindet das Steigrohr eine Höhe zwischen 9 und 10 m, so ist im Verdampfungsraum der erforderliche niedrige Druck vorhanden, bei dem das Grundwasser bei einer Temperatur zwischen 7 und 12°C verdampft. Nachdem typische Gebäude wenigstens 6 bis 8 m hoch sind, und nachdem in vielen Regionen das Grundwasser bereits bei 2 bis 4 m unter der Erdoberfläche vorhanden ist, führt die Installation eines solchen Rohrs zu keinem erheblichen zusätzlichen Aufwand, da nur etwas tiefer als für das Hausfundament gegraben werden muss, und da typische Gebäudehöhen ohne weiteres so hoch sind, dass das Steigrohr bzw. die Verdampfungskammer nicht über das Gebäude hinaus vorsteht.In a preferred embodiment, a completely open circuit is used in which groundwater is brought to the low pressure. A preferred embodiment for generating a pressure below 20 hPa for groundwater is the simple use of a riser, which in a pressure-tight evaporation chamber opens. If the riser crosses a height between 9 and 10 m, then the required low pressure is present in the evaporation space, at which the groundwater evaporates at a temperature between 7 and 12 ° C. After typical buildings are at least 6 to 8 meters high, and since in many regions the groundwater already at 2 to 4 m below the surface, the installation of such a pipe does not lead to significant additional effort, as only slightly lower than for the house foundation must be dug, and because typical building heights are readily so high that the riser or the evaporation chamber does not protrude beyond the building.
Für Anwendungsfälle, bei denen nur ein kürzeres Steigrohr möglich ist, kann die Länge des Steigrohrs ohne weiteres durch eine Pumpen/Turbinenkombination reduziert werden, die aufgrund der Tatsache, dass die Turbine für die Umsetzung vom hohen auf den niedrigen Druck und die Pumpe für die Umsetzung von dem niedrigen Druck auf den hohen Druck verwendet wird, nur eine geringe zusätzliche Arbeit von außen benötigt.For applications where only a shorter riser is possible, the length of the riser can be readily reduced by a pump / turbine combination, due to the fact that the turbine is designed for high to low pressure conversion and the pump for conversion used by the low pressure on the high pressure, only a little extra work needed from the outside.
Damit werden Primär-Wärmetauscherverluste eliminiert, da kein Primär-Wärmetauscher eingesetzt wird, sondern das verdampfte Grundwasser direkt als Arbeitsdampf bzw. Arbeitsmittel verwendet wird.This primary heat exchanger losses are eliminated because no primary heat exchanger is used, but the evaporated groundwater is used directly as working steam or working fluid.
Bei einem bevorzugten Ausführungsbeispiel wird auch im Verflüssiger kein Wärmetauscher verwendet. Statt dessen wird der aufgrund seiner Kompression erhitzte Wasserdampf direkt in einem Verflüssiger in das Heizungswasser eingeführt, so dass innerhalb des Wassers eine Verflüssigung des Wasserdampfes stattfindet, derart, dass auch Sekundär-Wärmetauscher-Verluste eliminiert sind.In a preferred embodiment, no heat exchanger is used in the condenser. Instead, the water vapor heated due to its compression is introduced directly into the heating water in a condenser, so that liquefaction of the water vapor takes place within the water, such that secondary heat exchanger losses are also eliminated.
Die erfindungsgemäße Wasserverdampfer-Strömungsmaschinen-Verflüssiger-Kombination ermöglicht somit im Vergleich zu üblichen Wärmepumpen Wirkungsgrade von mindestens Faktor 6. Es kann also mindestens das 5-fache der bei der Verdichtung aufgewendeten elektrischen Energie aus dem Grundwasser entzogen werden, so dass selbst dann, wenn die Strömungsmaschine mit elektrischem Strom betrieben wird, eine Heizenergie von 240 % = 6 40 % bezogen auf den Primärenergieträger bereitgestellt wird. Dies ist mindestens eine Verdopplung der Effizienz verglichen mit dem Stand der Technik, oder verglichen mit den Energiekosten eine Halbierung. Dies gilt insbesondere auch für den klimarelevanten Ausstoß von Kohlendioxid.The water evaporator fluid machine condenser combination according to the invention thus enables efficiencies of at least factor 6 in comparison to conventional heat pumps. Thus, at least 5 times the electrical energy expended in the compression can be extracted from the groundwater be so that even if the turbomachine is operated with electric current, a heating energy of 240% = 6 40% based on the primary energy carrier is provided. This is at least a doubling of efficiency compared to the prior art, or halved compared to energy costs. This applies in particular to climate-relevant emissions of carbon dioxide.
Bevorzugte Ausführungsbeispiele der vorliegenden Erfindung werden nachfolgend bezugnehmend auf die beiliegenden Zeichnungen detailliert erläutert. Es zeigen:
- Fig. 1a
- ein prinzipielles Blockschaltbild der erfindungsgemä- ßen Wärmepumpe;
- Fig. 1b
- eine Tabelle zur Illustration verschiedener Drücke und der diesen Drücken zugeordneten Verdampfungstem- peraturen;
- Fig. 2
- ein Blockschaltbild eines bevorzugten Ausführungsbei- spiels der erfindungsgemäßen Wärmepumpe, die mit Grundwasser, Meerwasser, Flusswasser, Seewasser oder Sole betrieben wird;
- Fig. 3a
- eine alternative Ausführungsform des Verflüssigers von
Fig. 2 ; - Fig. 3b
- eine alternative Ausführungsform des Verflüssigers mit reduziertem Rücklauf im Aus-Betrieb;
- Fig. 3c
- eine schematische Darstellung des Verflüssigers mit einem Gasabscheider;
- Fig. 4a
- eine bevorzugte Implementierung des Verdampfers von
Fig. 2 ; - Fig. 4b
- eine alternative Ausführungsform des Verdampfers mit Verwendung des Verflüssiger-Ablaufs als Siedeunter- stützung;
- Fig. 4c
- eine alternative Ausführungsform des Verdampfers mit einem Wärmetauscher zur Verwendung von Grundwasser zur Siedeunterstützung;
- Fig. 4d
- eine alternative Ausführungsform des Verdampfers mit Einspeisung von der Seite und Ablauf in der Mitte;
- Fig. 4e
- eine schematische Darstellung des Aufweiters mit An- gabe bevorzugter Maße;
- Fig. 5a
- eine alternative Implementierung des Verdampfers zur Reduzierung der Höhe des Steigrohrs;
- Fig. 5b
- eine Implementierung einer alternativen Realisierung eines Anschlusses einer Heizungsleitung an den Verflüssiger mit einer Turbinen/Pumpenkombination;
- Fig. 6a
- eine schematische Darstellung des Verdichters ausge- führt durch mehrere hintereinander angeordnete Strö- mungsmaschinen;
- Fig. 6b
- eine schematische Darstellung der Einstellung der Drehzahlen von zwei kaskadierten Strömungsmaschinen in Abhängigkeit von der Soll-Temperatur;
- Fig. 6c
- eine schematische Draufsicht eines Radialrads einer Strömungsmaschine gemäß einem bevorzugten Ausfüh- rungsbeispiel der vorliegenden Erfindung;
- Fig. 6d
- eine schematische Querschnittsansicht mit einer le- diglich schematischen Darstellung der Radialrad- Schaufeln zur Veranschaulichung der unterschiedlichen Erstreckung der Schaufeln im Hinblick auf den Radius des Radialrads;
- Fig. 7
- ein beispielhaftes h, log p-Diagramm; und
- Fig. 8
- eine bekannte Wärmepumpe, die den linksläufigen Kreislauf von
Fig. 7 durchführt.
- Fig. 1a
- a schematic block diagram of the inventive heat pump;
- Fig. 1b
- a table illustrating various pressures and the evaporation temperatures associated with these pressures;
- Fig. 2
- a block diagram of a preferred exemplary embodiment of the heat pump according to the invention, which is operated with groundwater, seawater, river water, seawater or brine;
- Fig. 3a
- an alternative embodiment of the condenser of
Fig. 2 ; - Fig. 3b
- an alternative embodiment of the condenser with reduced return in off mode;
- Fig. 3c
- a schematic representation of the condenser with a gas separator;
- Fig. 4a
- a preferred implementation of the evaporator of
Fig. 2 ; - Fig. 4b
- an alternative embodiment of the evaporator with the use of the condenser drain as Siedeunter- support;
- Fig. 4c
- an alternative embodiment of the evaporator with a heat exchanger for use of groundwater for Siedeunterstützung;
- Fig. 4d
- an alternative embodiment of the evaporator with feed from the side and drain in the middle;
- Fig. 4e
- a schematic representation of the expander with indication of preferred dimensions;
- Fig. 5a
- an alternative implementation of the evaporator to reduce the height of the riser;
- Fig. 5b
- an implementation of an alternative implementation of a connection of a heating line to the condenser with a turbine / pump combination;
- Fig. 6a
- a schematic representation of the compressor performed by several sequentially arranged flow machines;
- Fig. 6b
- a schematic representation of the setting of the rotational speeds of two cascaded turbomachines in dependence on the target temperature;
- Fig. 6c
- a schematic plan view of a radial impeller of a turbomachine according to a preferred embodiment of the present invention;
- Fig. 6d
- a schematic cross-sectional view with a merely schematic representation of the Radialrad- blades to illustrate the different extent of the blades with respect to the radius of the radial wheel;
- Fig. 7
- an exemplary h, log p diagram; and
- Fig. 8
- a well-known heat pump, the left-handed cycle of
Fig. 7 performs.
Der Wasserdampf wird durch die Saugleitung 12 einem Verdichter/Verflüssiger-System 14 zugeführt, das eine Strömungsmaschine wie z. B. einen Radialverdichter, beispielsweise in Form eines Turboverdichters aufweist, der in
Die Strömungsmaschine ist mit einem Verflüssiger 18 gekoppelt, der ausgebildet ist, um den verdichteten Arbeitsdampf zu verflüssigen. Durch das Verflüssigen wird die in dem Arbeitsdampf enthaltene Energie dem Verflüssiger 18 zugeführt, um dann über den Vorlauf 20a einem Heizsystem zugeführt zu werden. Über den Rücklauf 20b fließt das Arbeitsfluid wieder in den Verflüssiger zurück.The turbomachine is coupled to a
Erfindungsgemäß wird es bevorzugt, dem energiereichen Wasserdampf direkt durch das kältere Heizungswasser die Wärme (-energie) zu entziehen, welche vom Heizungswasser aufgenommen wird, so dass dieses sich erwärmt. Dem Dampf wird hierbei so viel Energie entzogen, dass dieser verflüssigt wird und ebenfalls am Heizungskreislauf teilnimmt.According to the invention, it is preferable to extract from the high-energy steam directly through the colder heating water the heat (energy) which is taken up by the heating water so that it heats up. The steam is so much energy withdrawn that this is liquefied and also participates in the heating circuit.
Damit findet ein Materialeintrag in den Verflüssiger bzw. das Heizungssystem statt, der durch einen Ablauf 22 reguliert wird, derart, dass der Verflüssiger in seinem Verflüssigerraum einen Wasserstand hat, der trotz des ständigen Zuführens von Wasserdampf und damit Kondensat immer unterhalb eines Maximalpegels bleibt.Thus, a material entry into the condenser or the heating system takes place, which is regulated by a
Wie es bereits ausgeführt worden ist, wird es bevorzugt, einen offenen Kreislauf zu nehmen, also das Wasser, das die Wärmequelle darstellt, direkt ohne Wärmetauscher zu verdampfen. Alternativ könnte jedoch auch das zu verdampfende Wasser zunächst über einen Wärmetauscher von einer externen Wärmequelle aufgeheizt werden. Dabei ist jedoch zu bedenken, dass dieser Wärmetauscher wieder Verluste und apparativen Aufwand bedeutet.
Darüber hinaus wird es bevorzugt, um auch Verluste für den zweiten Wärmetauscher, der auf Verflüssiger-Seite bisher notwendigerweise vorhanden ist, zu vermeiden, auch dort das Medium direkt zu verwenden, also, wenn an ein Haus mit Fußbodenheizung gedacht wird, das Wasser, das von dem Verdampfer stammt, direkt in der Fußbodenheizung zirkulieren zu lassen.As has already been stated, it is preferred to take an open circuit, ie to evaporate the water, which is the heat source, directly without a heat exchanger. Alternatively, however, the water to be evaporated could first be heated by a heat exchanger from an external heat source. However, it should be remembered that this heat exchanger again means losses and equipment expense.
Moreover, in order to avoid losses for the second heat exchanger, which has hitherto necessarily been present on the condenser side, it is also preferred to use the medium directly there as well, that is to say to a house with underfloor heating It is thought that the water coming from the evaporator should be circulated directly in the underfloor heating.
Alternativ kann jedoch auch auf Verflüssiger-Seite ein Wärmetauscher angeordnet werden, der mit dem Vorlauf 20a gespeist wird und der den Rücklauf 20b aufweist, wobei dieser Wärmetauscher das im Verflüssiger befindliche Wasser abkühlt und damit eine separate Fußbodenheizungsflüssigkeit, die typischerweise Wasser sein wird, aufheizt.Alternatively, however, on the condenser side, a heat exchanger can be arranged, which is fed with the
Aufgrund der Tatsache, dass als Arbeitsmedium Wasser verwendet wird, und aufgrund der Tatsache, dass von dem Grundwasser nur der verdampfte Anteil in die Strömungsmaschine eingespeist wird, spielt der Reinheitsgrad des Wassers keine Rolle. Die Strömungsmaschine wird, genauso wie der Verflüssiger und die ggf. direkt gekoppelte Fußbodenheizung immer mit destilliertem Wasser versorgt, derart, dass das System im Vergleich zu heutigen Systemen einen reduzierten Wartungsaufwand hat. Anders ausgedrückt ist das System selbstreinigend, da dem System immer nur destilliertes Wasser zugeführt wird und das Wasser im Ablauf 22 somit nicht verschmutzt ist.Due to the fact that water is used as the working medium, and due to the fact that only the evaporated portion of the groundwater is fed into the turbomachine, the purity of the water does not matter. The turbomachine, as well as the condenser and possibly directly coupled underfloor heating always supplied with distilled water, so that the system has a reduced maintenance compared to today's systems. In other words, the system is self-cleaning, since the system is always fed only distilled water and the water in the
Darüber hinaus sei darauf hingewiesen, dass Strömungsmaschinen die Eigenschaften haben, dass sie - ähnlich einer Flugzeugturbine - das verdichtete Medium nicht mit problematischen Stoffen, wie beispielsweise Öl, in Verbindung bringen. Statt dessen wird der Wasserdampf lediglich durch die Turbine bzw. den Turboverdichter verdichtet, jedoch nicht mit Öl oder einem sonstigen Reinheits-beeinträchtigenden Medium in Verbindung gebracht und damit verunreinigt.In addition, it should be noted that turbomachines have the properties that they - similar to an aircraft turbine - the compressed medium not with problematic substances, such as oil, in connection. Instead, the water vapor is compressed only by the turbine or the turbo compressor, but not associated with oil or other purity-impairing medium and thus contaminated.
Das durch den Ablauf abgeführte destillierte Wasser kann somit - wenn keine sonstigen Vorschriften im Wege stehen - ohne weiteres dem Grundwasser wieder zugeführt werden. Alternativ kann es hier jedoch auch z. B. im Garten oder in einer Freifläche versickert werden, oder es kann über den Kanal, sofern dies Vorschriften gebieten - einer Kläranlage zugeführt werden.The distilled water discharged through the drain can thus - if no other regulations stand in the way - be easily returned to the groundwater. Alternatively, however, it may also be z. B. in the garden or in an open space to be seeped, or it can be supplied via the channel, if regulations dictate - a sewage treatment plant.
Die erfindungsgemäße Kombination von Wasser als Arbeitsmittel mit dem um das 2-fache besseren nutzbaren Enthalpie-Differenz-Verhältnis im Vergleich zu R134a und aufgrund der damit reduzierten Anforderungen an die Geschlossenheit des Systems (es wird vielmehr ein offenes System bevorzugt), und aufgrund des Einsatzes der Strömungsmaschine, durch den effizient und ohne Reinheitsbeeinträchtigungen die erforderlichen Verdichtungsfaktoren erreicht werden, wird ein effizienter und umweltneutraler Wärmepumpenprozess geschaffen, der dann, wenn im Verflüssiger der Wasserdampf direkt verflüssigt wird, noch effizienter wird, da dann im gesamten Wärmepumpenprozess kein einziger Wärmetauscher mehr benötigt wird.The combination according to the invention of water as a working medium with the two times better usable enthalpy difference ratio compared to R134a and due to the reduced requirements for the closed system (rather an open system is preferred), and because of the use the turbomachine, through which the required compression factors are achieved efficiently and without purity impairments, an efficient and environmentally neutral heat pump process is created, which is even more efficient if the liquefier in the liquefier directly liquefied, since then no heat exchanger is needed in the entire heat pump process ,
Darüber hinaus fallen sämtliche mit der Kolbenverdichtung verbundenen Verluste weg. Zudem können die bei Wasser sehr gering ausfallenden Verluste, die sonst bei der Drosselung anfallen, dazu verwendet werden, den Verdampfungsprozess zu verbessern, da das Ablaufwasser mit der Ablauftemperatur, die typischerweise höher als die Grundwasser-Temperatur sein wird, vorteilhaft verwendet werden, um im Verdampfer mittels einer Strukturierung 206 eines Ablaufrohrs 204, wie es in
Nachfolgend wird bezugnehmend auf
Das Steigrohr ist in einem Steigrohrbecken 116 angeordnet, das von einer vorzugsweise vorgesehenen Pumpe 118 mit Wasser gefüllt wird. Die Pegel in 116 und 108 sind nach dem Prinzip der kommunizierenden Röhren miteinander verbunden, wobei die Schwerkraft und die unterschiedlichen Drücke in 116 und 108 für einen Transport des Wassers von 116 nach 108 sorgen. Der Wasserpegel im Steigrohrbecken 116 ist vorzugsweise so angeordnet, dass auch bei unterschiedlichen Luftdrücken der Pegel nie unter den Einlass des Steigrohrs 102 fällt, damit ein Eindringen von Luft vermieden wird.The riser is arranged in a
Vorzugsweise umfasst der Verdampfer 10 einen Gasabscheider, der ausgebildet ist, um wenigstens einen Teil, z. B. wenigstens 50 % eines Gases, das in dem zu verdampfenden Wasser gelöst ist, aus dem zu verdampfenden Wasser zu entfernen, so dass der entfernte Teil des Gases nicht über den Verdampfungsraum von dem Verdichter angesaugt wird. Vorzugsweise ist der Gasabscheider angeordnet, um den entfernten Teil des Gases einem nicht verdampften Wasser zuzuführen, damit das Gas von dem nicht verdampften Wasser abtransportiert wird. Gelöste Gase können Sauerstoff, Kohlendioxid, Stickstoff etc. umfassen. Diese Gase verdampfen zumeist bei einem höheren Druck als Wasser so dass der Gasabscheider unterhalb des Aufweiters 108 angeordnet sein kann, so dass im Gasabscheider verdampfter Sauerstoff etc. aus dem gerade noch nicht verdampfenden Wasser austritt und vorzugsweise in die Rückleitung 113 eingespeist wird. Die Einspeisung erfolgt vorzugsweise an der Stelle des Rückleitung 113, an der der Druck so niedrig ist, dass das Gas von dem zurücklaufenden Wasser wieder ins Grundwasser mitgenommen wird. Alternativ kann das abgeschiedene Gas jedoch auch gesammelt und in bestimmten Intervallen entsorgt werden oder laufend entlüftet, also an die Atmosphäre abgegeben werden.Preferably, the
Typischweise wird das Grundwasser, Meerwasser, Flusswasser, Seewasser, die Sole oder eine sonstige in der Natur vorkommende wässrige Lösung eine Temperatur zwischen 8°C und 12°C haben. Durch die Absenkung der Temperatur von 1 l Wasser um 1°C kann eine Leistung von 4,2 kW erzeugt werden. Wird das Wasser um 2,5°C abgekühlt, so wird eine Leistung von 10,5 kW erzeugt. Vorzugsweise wird das Steigrohr von einem Wasserstrom mit einer Stromstärke in Abhängigkeit von der Heizleistung durchströmt, im Beispiel ein Liter pro Sekunde.Typically, the groundwater, seawater, river water, seawater, brine or any other naturally occurring aqueous solution will have a temperature between 8 ° C and 12 ° C. By lowering the temperature of 1 liter of water by 1 ° C, a power of 4.2 kW can be generated. If the water is cooled by 2.5 ° C, a power of 10.5 kW is generated. Preferably, the riser is flowed through by a stream of water with a current in dependence on the heating power, in the example one liter per second.
Wenn die Wärmepumpe auf relativ hoher Last arbeitet, wird der Verdampfer etwa 6 ml pro Sekunde verdampfen, was einem Dampfvolumen von ca. 1,2 Kubikmeter pro Sekunde entspricht. Je nach geforderter Heizungswassertemperatur wird die Strömungsmaschine im Hinblick auf ihre Verdichtungsleistung gesteuert. Wird eine Heizungs-Vorlauftemperatur von 45°C gewünscht, was selbst für extrem kalte Tage bei weitem ausreicht, so muss die Strömungsmaschine den bei vielleicht 10 hPa erzeugten Dampf auf einen Druck von 100 hPa erhöhen. Reicht dagegen eine Vorlauftemperatur von z. B. 25° für die Fußbodenheizung, so muss nur um einen Faktor 3 durch die Strömungsmaschine verdichtet werden.When the heat pump is operating at a relatively high load, the evaporator will vaporize about 6 ml per second, which corresponds to a vapor volume of about 1.2 cubic meters per second. Depending on the required heating water temperature, the turbomachine is controlled with regard to its compaction performance. If a heating flow temperature of 45 ° C is desired, which is by far sufficient even for extremely cold days, then the turbomachine must increase the steam produced at perhaps 10 hPa to a pressure of 100 hPa. In contrast, a flow temperature of z. B. 25 ° for underfloor heating, so only by a factor of 3 must be compressed by the turbomachine.
Die erzeugte Leistung wird daher durch die Verdichterleistung bestimmt, also zum einen durch den Verdichtungsfaktor, also wie stark der Verdichter verdichtet, und zum anderen durch von dem Verdichter erzeugten Volumenstrom. Erhöht sich der Volumenstrom, so muss der Verdampfer mehr verdampfen, wobei die Pumpe 118 mehr Grundwasser in das Steigrohrbecken 116 befördert, so dass der Verdampfungskammer mehr Grundwasser zugeführt wird. Wird die Strömungsmaschine dagegen einen geringeren Verdichtungsfaktor liefern, so fließt auch weniger Grundwasser von unten nach oben.The power generated is therefore determined by the compressor power, so on the one hand by the compression factor, ie how much compressed the compressor, and on the other by the volume flow generated by the compressor. As the volumetric flow increases, the evaporator must vaporize more, with the
An dieser Stelle sei jedoch darauf hingewiesen, dass es bevorzugt wird, den Durchfluss von Grundwasser durch die Pumpe 118 zu steuern. Nach dem Prinzip der kommunizierenden Röhren legt der Füllstand im Behälter 116 bzw. die Fördermenge der Pumpe 118 den Durchfluss durch das Steigrohr fest. Damit kann eine Effizienzsteigerung der Anlage erreicht werden, da die Steuerung des Durchflusses von der Saugleistung der Strömungsmaschine entkoppelt wird.It should be noted, however, that it is preferred to control the flow of groundwater through the
Es wird keine Pumpe benötigt, um das Grundwasser von unten in die Verdampfungskammer 100 zu pumpen. Statt dessen geschieht dies von "selbst". Dieses automatische Aufsteigen zur evakuierten Verdampfungskammer hilft auch dabei, dass der Unterdruck von 20 hPa ohne Weiteres erreichbar ist. Hierzu werden keine Evakuierungspumpen oder etwas ähnliches benötigt. Statt dessen wird lediglich ein Steigrohr mit einer Höhe größer 9 m benötigt. Dann wird eine rein passive Unterdruckerzeugung erreicht. Der nötige Unterdruck kann jedoch auch mit einem wesentlich kürzeren Steigrohr erzeugt werden, wenn z. B. die Implementierung von
Bei dem bevorzugten Ausführungsbeispiel ist die Strömungsmaschine als Radialverdichter mit drehbarem Rad ausgeführt, wobei das Rad ein langsamläufiges Radialrad, ein mittelläufiges Radialrad, ein Halbaxialrad oder ein Axialrad bzw. ein Propeller sein kann, wie es in der Technik bekannt sind. Radialverdichter sind in "Strömungsmaschinen", C. Pfleiderer, H. Petermann, Springer-Verlag, 2005, Seiten 82 und 83 beschrieben. Solche Radialverdichter umfassen somit als drehbares Rad den sog. Mittelläufer, dessen Form von den einzelnen Anforderungen abhängt. Generell können beliebige Strömungsmaschinen eingesetzt werden, wie sie als Turboverdichter, Ventilatoren, Gebläse oder Turbokompressoren bekannt sind.In the preferred embodiment, the turbomachine is configured as a rotary compressor with a rotatable wheel, wherein the wheel may be a low-speed radial, medium-radial, semi-axial, or propeller, as known in the art. Radial compressors are described in "Turbomachines", C. Pfleiderer, H. Petermann, Springer-Verlag, 2005,
Bei dem bevorzugten Ausführungsbeispiel der vorliegenden Erfindung ist der Radial-Verdichter 16 als mehrere unabhängige Strömungsmaschinen ausgeführt, die zumindest im Hinblick auf ihre Drehzahl unabhängig voneinander gesteuert werden können, so dass zwei Strömungsmaschinen unterschiedliche Drehzahlen haben können. Eine solche Implementierung ist in
Die kaskadierten unabhängig voneinander betriebenen Strömungsmaschinen werden vorzugsweise von einer Steuerung 250 angesteuert, die eingangsseitig eine Soll-Temperatur im Heizkreis sowie gegebenenfalls auch eine Ist-Temperatur im Heizkreis erhält. Abhängig von der gewünschten Soll-Temperatur werden die Drehzahl einer in der Kaskade früher angeordneten Strömungsmaschine, die beispielhaft mit n1 bezeichnet ist, und die Drehzahl n2 einer später in der Kaskade angeordneten Strömungsmaschine so geändert, wie es anhand von
Der Schnittpunkt zwischen den einzeln aufgetragenen Drehzahlen n1 und n2 kann an beliebiger Stelle, also an beliebiger Soll-Temperatur erfolgen und kann gegebenenfalls auch nicht erfolgen. Generell wird jedoch bevorzugt, eine in der Kaskade näher am Verflüssiger angeordnete Strömungsmaschine im Hinblick auf ihre Drehzahl stärker anzuheben als eine früher in der Kaskade angeordnete Strömungsmaschine, wenn eine höhere Soll-Temperatur gewünscht wird.The intersection between the individually applied rotational speeds n 1 and n 2 can take place at any desired point, that is to say at any desired temperature and, if appropriate, can not take place. In general, however, it is preferable to lift a turbomachine arranged closer to the condenser in the cascade more strongly in terms of its rotational speed than a turbomachine arranged earlier in the cascade, if a higher desired temperature is desired.
Der Grund hierfür besteht darin, dass die später in der Kaskade angeordnete Strömungsmaschine bereits verdichtetes Gas, das von einer früher in der Kaskade angeordneten Strömungsmaschine verdichtet worden ist, weiterverarbeiten muss. Ferner stellt dies sicher, dass der Schaufelwinkel von Schaufeln eines Radialrads, wie es auch Bezug nehmend auf
Im Hinblick darauf wird es ferner bevorzugt, dass eine in der Kaskade mehr in Richtung des Verflüssigers angeordnete Strömungsmaschine eine Drehrichtung des Radialrads aufweist, die zu der Drehrichtung eines früher in der Kaskade angeordneten Radialrads entgegengesetzt ist. Damit kann ein nahezu optimaler Eintrittswinkel der Schaufeln beider Axialräder in den Gasstrom erreicht werden, derart, dass ein günstiger Wirkungsgrad der Strömungsmaschinen-Kaskade nicht nur in einem kleinen Soll-Temperaturbereich auftritt, sondern in einem wesentlich größeren Soll-Temperaturbereich zwischen 20 und 50 Grad, was für typische Heizungsanwendungen ein optimaler Bereich ist. Die erfindungsgemäße Drehzahlsteuerung sowie gegebenenfalls die Verwendung von gegenläufigen Axialrädern liefert somit eine optimale Abstimmung zwischen dem variablen Gasstrom bei sich verändernder Soll-Temperatur einerseits und den festen Schaufelwinkeln der Axialräder andererseits.In view of this, it is further preferred that a turbomachine arranged more in the cascade in the direction of the condenser has a direction of rotation of the radial wheel which is opposite to the direction of rotation of a radial wheel previously arranged in the cascade. Thus, a nearly optimal entry angle of the blades of both axial wheels can be achieved in the gas flow, such that a favorable efficiency of the turbomachine cascade occurs not only in a small target temperature range, but in a much larger target temperature range between 20 and 50 degrees, which is an optimal range for typical heating applications. The speed control according to the invention and, where appropriate, the use of counter-rotating axial gears thus provides an optimal match between the variable gas flow with changing target temperature on the one hand and the fixed blade angles of the axial wheels on the other.
Bei bevorzugten Ausführungsbeispielen der vorliegenden Erfindung wird zumindest eines oder vorzugsweise sämtliche Axialräder aller Strömungsmaschinen aus Kunststoff mit einer Zugfestigkeit oberhalb 80 MPa hergestellt. Ein bevorzugter Kunststoff hierfür ist Polyamid 6.6 mit eingelegten Karbonfasern. Dieser Kunststoff hat den Vorteil der Zugfestigkeit, so dass Axialräder der Störungsmaschinen aus diesem Kunststoff hergestellt werden können und dennoch mit hohen Drehzahlen betrieben werden können.In preferred embodiments of the present invention, at least one or preferably all of the axial gears of all flow machines are made of plastic having a tensile strength above 80 MPa. A preferred plastic this is polyamide 6.6 with inserted carbon fibers. This plastic has the advantage of tensile strength, so that Axialräder the fault machines can be made of this plastic and yet can be operated at high speeds.
Vorzugsweise werden Axialräder erfindungsgemäß eingesetzt, wie sie beispielsweise in
Wenn
Eine beliebig dichte Anbringung von sich von innen, also vom Radius rw nach außen erstreckenden Schaufeln ist jedoch aus technischen Gründen nicht möglich, da dann die Ansaugöffnung mit dem Radius r1 mehr und mehr blockiert wird.However, for technical reasons, an arbitrarily tight attachment of from the inside, ie from the radius r w outwardly extending blades is not possible because then the suction port with the radius r 1 is more and more blocked.
Erfindungsgemäß wird es daher bevorzugt, Schaufeln 272 bzw. 274 bzw. 276 vorzusehen, die sich weniger lang als die Schaufel 262 erstrecken. Insbesondere erstrecken sich die Schaufeln 272 nicht von rw bis ganz nach außen, sondern von R1 nach außen bezüglich des Radialrads, wobei R1 größer als rw ist. Analog hierzu erstrecken sich, wie es in
Diese Verhältnisse sind in
Vorzugsweise ist somit zwischen zwei sich tiefer nach innen erstreckenden Schaufeln wenigstens eine Schaufel angeordnet, die sich nicht so weit nach innen erstreckt. Dies führt dazu, dass der Ansaugbereich nicht verstopft wird bzw. Bereiche mit kleinerem Radius nicht zu stark mit Schaufeln belegt werden, während Bereiche mit größerem Radius dichter mit Schaufeln belegt werden, so dass am Ausgang des Radialrads, also dort, wo das komprimierte Gas das Radialrad verlässt, eine möglichst homogene Geschwindigkeitsverteilung des austretenden Gases existiert. Die Geschwindigkeitsverteilung des austretenden Gases ist bei dem erfindungsgemäßen bevorzugten Radialrad in
An dieser Stelle sei darauf hingewiesen, dass die relativ aufwendige und komplizierte Form des Radialrads in
An dieser Stelle sei darauf hingewiesen, dass sehr hohe Drehzahlen des Radialrads bevorzugt werden, so dass die auf die Schaufeln wirkenden Beschleunigungen ganz erhebliche Werte annehmen. Aus diesem Grund wird es bevorzugt, dass insbesondere die kürzeren Schaufeln 272, 274, 276 nicht nur mit der Basis, sondern auch mit dem Deckel fest verbunden sind, derart, dass das Radialrad die auftretenden Beschleunigungen ohne weiteres aushalten kann.It should be noted at this point that very high rotational speeds of the radial wheel are preferred, so that the accelerations acting on the blades assume very considerable values. For this reason, it is preferred that, in particular, the
In diesem Zusammenhang sei auch darauf hingewiesen, dass die Verwendung von Kunststoff auch aufgrund der überragenden Schlagfestigkeit von Kunststoff günstig ist. So ist nicht immer auszuschließen dass Eiskristalle oder Wassertröpfchen auf das Radialrad zumindest der ersten Verdichterstufe aufschlagen. Aufgrund der hohen Beschleunigungen entstehen hier sehr hohe Aufprallkräfte, die von Kunststoffen mit ausreichender Schlagfestigkeit ohne weiteres ausgehalten werden. Des Weiteren findet die Verflüssigung im Verflüssiger bevorzugt aufgrund des Kavitations-Prinzips statt. Hier fallen Dampfbläschen aufgrund dieses Prinzips in einem Wasservolumen in sich zusammen. Dort entstehen ebenfalls mikroskopisch betrachtet ganz erhebliche Geschwindigkeiten und Kräfte, die auf lange Sicht betrachtet zu Materialermüdungen führen können, welche jedoch dann, wenn ein Kunststoff mit einer ausreichender Schlagfestigkeit eingesetzt wird, leicht beherrschbar sind.In this context, it should also be noted that the use of plastic is also favorable due to the superior impact resistance of plastic. So it is not always ruled out that ice crystals or water droplets hit the radial wheel at least the first compressor stage. Due to the high accelerations, very high impact forces arise here, which are easily withstood by plastics with sufficient impact resistance. Furthermore, the liquefaction in the liquefier preferably takes place on the basis of the cavitation principle. Here steam bubbles fall due to this principle in a volume of water in itself. There are also microscopically quite considerable velocities and forces arising over the long term Seen view can lead to material fatigue, which, however, when a plastic is used with a sufficient impact resistance, are easily manageable.
Das von dem letzten Verdichter 174 ausgegebene verdichtete Gas, also der verdichtete Wasserdampf wird dann dem Verflüssiger 18 zugeführt, der ausgestaltet sein kann, wie es in
Die Ausführungsform in
Nachdem aufgrund des ständig in den Verflüssiger eingeführten Dampfes der Wasserstand im Verflüssiger immer mehr ansteigen würde, ist der Ablauf 22 vorgesehen, über dem, damit der Wasserstand im Verflüssiger sich im Wesentlichen nicht verändert, ebenfalls z. B. etwa 4 ml pro Sekunde abfließen müssen. Hierzu ist eine Ablauf-Pumpe bzw. ein Ablaufventil 192 zur Druckregelung vorgesehen, derart, dass ohne Druckverlust die erforderliche Menge von z. B. 4 ml pro Sekunde, also die Menge, die an Wasserdampf dem Verflüssiger bei laufendem Verdichter zugeführt wird, wieder abgeführt wird. Je nach Implementierung kann der Ablauf in das Steigrohr eingeführt werden, wie es bei 194 gezeigt ist. Nachdem entlang des Steigrohrs 102 sämtliche Drücke zwischen einem bar und dem im Verdampfungsraum vorhandenen Druck vorliegen, wird es bevorzugt, den Ablauf 22 an der Stelle 194 in das Steigrohr einzuspeisen, an dem annähernd der gleiche Druck existiert wie er nach der Pumpe 192 bzw. dem Ventil 192 vorliegt. Dann muss keine Arbeit verrichtet werden, um das Ablaufwasser dem Steigrohr wieder zuzuführen.After due to the constantly introduced into the condenser, the water level in the condenser would increase more and more, the
Bei dem in
Allerdings kann der Rücklauf 112 aus dem Verdampfer ohne Probleme in das Grundwasser eingespeist werden, da das dort zurücklaufende Wasser lediglich mit dem Steigrohr und der Rückleitung in Kontakt war, jedoch die "Verdampfungsgrenze" zwischen dem Verdampfungs-Aufweiter 108 und dem Ausgang zur Strömungsmaschine nicht überschritten hat.However, the
Es sei darauf hingewiesen, dass der Verdampfungsraum bei dem in
Nachfolgend wird auf
Ferner wird es bevorzugt, um den Verflüssiger herum eine Schalldämmung 208 vorzusehen, die aktiv oder passiv ausgebildet sein kann. Eine passive Schalldämmung wird ähnlich einer Wärmedämmung die Frequenzen des durch das Verflüssigen erzeugten Schalls so gut als möglich dämmen. Genauso wird es auch bevorzugt, die anderen Komponenten des Systems schallzudämmen.Further, it is preferred to provide around the condenser a
Die Schalldämmung kann alternativ auch aktiv ausgebildet sein, wobei sie in diesem Fall z. B. ein Mikrophon zur Schallmessung hätte und ansprechend darauf eine Schall-Gegenwirkung auslösen würde, wie beispielsweise eine In-Vibration-Versetzen einer äußeren Verflüssiger-Wand etc. mit z. B. piezoelektrischen Mitteln.The sound insulation may alternatively be actively formed, in which case z. B. would have a microphone for sound measurement and in response would trigger a sound-counteraction, such as an in-vibration displacement of an outer condenser wall, etc. with z. B. piezoelectric means.
Das in
Erst dann wird ein Dampf im Verflüssiger zur Kondensierung gebracht, wenn ein genügender Anteil des Wassers aus der Leitung 198 entfernt worden ist. Ein solchermaßen geartetes Ausführungsbeispiel hat somit eine gewisse Verzögerungszeit, die benötigt wird, bis das Wasservolumen 180 wieder vom komprimierten Dampf aufgewärmt wird. Ferner ist die Arbeit, die benötigt wird, um das in die Leitung 198 eingedrungene Wasser aus der Leitung 198 wieder zu entfernen, nicht mehr wiedergewinnbar und somit im Hinblick auf die Heizung "verloren", derart, dass kleinere Wirkungsgrad-Einbußen in Kauf genommen werden müssen.Only then is a vapor in the condenser brought to condensation when a sufficient proportion of the water has been removed from the
Eine alternative Ausführungsform, die diese Problematik überwindet, ist in
Wenn bei der Implementierung von
Die Flussgeschwindigkeit am Rand des Aufweiters, also dort, wo der Pfeil 218 angedeutet ist, ist wesentlich geringer als in der Mitte. Es wird bevorzugt, den Verflüssiger als Temperaturschichtspeicher zu betreiben, derart, dass die Wärmepumpe und insbesondere der Verdichter nicht ununterbrochen laufen muss, sondern nur dann laufen muss, wenn Bedarf existiert, wie es für normale Heizungsanlagen, die z.B. mit einem Ölbrenner arbeiten, ebenfalls der Fall ist.The flow velocity at the edge of the expander, that is, where the
Nachdem das erfindungsgemäße System mit Wasser arbeitet, entstehen selbst bei starker Ausgasung keine Gase, die nicht bereits vorher im Grundwasser gelöst waren, so dass das abgeschiedene Gas keinerlei Umweltproblematik in sich birgt. Wieder wird betont, dass aufgrund des erfindungsgemäßen Strömungsmaschine-Verdichtens und des Verwendens von Wasser als Arbeitsflüssigkeit an keiner Stelle Kontaminationen bzw. Verschmutzungen durch ein synthetisches Kältemittel oder durch ein Öl aufgrund eines Ölkreislaufs auftreten. Das erfindungsgemäße System hat an jeder Stelle als Arbeitsmedium Wasser oder Dampf, welches wenigstens so sauber wie das ursprüngliche Grundwasser ist, oder sogar aufgrund der Verdampfung im Verdampfer noch sauberer als das Grundwasser ist, da es sich um destilliertes Wasser handelt, wenn der komprimierte Dampf im Verflüssiger wieder verflüssigt worden ist.After the system of the invention works with water, even with strong outgassing no gases that were not previously solved in the groundwater, so that the separated gas has no environmental problems in itself. Again, it is emphasized that due to the turbomachinery compaction according to the invention and the use of water as the working fluid at any point contamination or contamination by a synthetic refrigerant or by an oil due to an oil circuit occur. The system according to the invention has at each point as a working medium water or Steam which is at least as clean as the original groundwater, or even cleaner than the groundwater due to evaporation in the evaporator, since it is distilled water when the compressed steam in the condenser has been re-liquefied.
Nachfolgend wird Bezug nehmend auf
Zur Beschleunigung des Verdampfungsvorgangs kann alternativ oder zusätzlich auch ein Bereich des Verdampfers, auf dem sich zu verdampfendes Wasser befindet, also die Oberfläche des Aufweiters oder ein Teil davon, aus einem rauen Material ausgeführt sein, um Keime für die Blasensiedung zu liefern. Alternativ oder zusätzlich kann auch ein raues Gitter (nahe) unter der Wasseroberfläche des zu verdampfenden Wassers angeordnet werden.To accelerate the evaporation process, alternatively or additionally, a region of the evaporator on which water to be evaporated is located, that is to say the surface of the expander or a part thereof, may be made of a rough material in order to supply nuclei for nucleate boiling. Alternatively or additionally, a rough grid (near) can be arranged below the water surface of the water to be evaporated.
Die dort entstehenden Dampfblasen werden unmittelbar als Siede-Keime für das Verdampfer-Wasser, das über den Zulauf 102 gefördert wird, wirken. Damit kann ohne größere zusätzliche Maßnahmen eine effiziente Blasensiedung im Verdampfer getriggert werden, wobei diese Triggerung ähnlich zu
Das in
Existieren wasserrechtliche Auflagen oder sonstige Gründe, dass dies nicht zulässig ist, so kann das in
Der große Durchmesser d2 des Aufweiters liegt bei bevorzugten Ausführungsbeispielen zwischen 15 und 100 cm und ist bei besonders bevorzugten Ausführungsbeispielen kleiner als 25 cm. Die kleine Ausführung des Verdampfers ist möglich, wenn effiziente Maßnahmen zur Triggerung und Unterstützung der Blasensiedung eingesetzt werden, wie sie vorstehend erläutert worden sind. Zwischen dem kleinen Radius d1 und dem großen Radius d2 befindet sich ein Krümmungsbereich des Aufweiters, der vorzugsweise so gestaltet ist, dass sich in diesem Bereich eine laminare Strömung ergibt, die von einer schnellen Flussrate, für vorzugsweise im Bereich von 7 bis 40 cm pro Sekunde liegt, auf eine relativ kleine Flussrate am Rand des Aufweiters abgesenkt wird. Starke Diskontinuitäten der Flussrate, wie beispielsweise Wirbel im Bereich der Krümmungslinie oder "Sprudeleffekte" oberhalb des Zulaufs, wenn von oben auf den Aufweiter gesehen wird, werden vorzugsweise vermieden, da sie gegebenenfalls Wirkungsgrad-beeinträchtigend sein können.The large diameter d 2 of the expander is in preferred embodiments between 15 and 100 cm and is smaller than 25 cm in particularly preferred embodiments. The small version of the evaporator is possible when efficient measures for triggering and supporting the bubble boiling are used, as explained above. Between the small radius d 1 and the large radius d 2 there is a curvature region of the expander, which is preferably designed to give a laminar flow in this region which is of a fast flow rate, preferably in the range of 7 to 40 cm per second, is lowered to a relatively small flow rate at the edge of the expander. Strong flow rate discontinuities, such as vortices in the area of the line of curvature or "bubbling effects" above the inlet when viewed from the top of the expander, are preferably avoided as they may be detrimental to efficiency.
Bei besonders bevorzugten Ausführungsbeispielen hat der Aufweiter eine Form, die dazu führt, dass die Höhe des Wasserstands über der Aufweiter-Oberfläche kleiner als 15 mm ist und vorzugsweise zwischen 1 und 5 mm liegt. Es wird daher bevorzugt, einen Aufweiter 200 einzusetzen, der so ausgebildet ist, dass in mehr als 50 % der Fläche des Aufweiters, wenn derselbe von oben betrachtet wird, eine Wasserhöhe existiert, die kleiner als 15 mm ist. Damit kann über dem gesamten Bereich eine effiziente Verdampfung sichergestellt werden, die im Hinblick auf ihre Effizienz noch besonders erhöht wird, wenn Maßnahmen zur Triggerung der Blasensiedung eingesetzt werden.In particularly preferred embodiments, the expander has a shape which causes the height of the water level above the expander surface to be less than 15 mm and preferably between 1 and 5 mm. It is therefore preferred to use an
Die erfindungsgemäße Wärmepumpe dient somit zur effizienten Wärmeversorgung von Gebäuden und benötigt kein Arbeitsmittel mehr, das einen Weltklima-schädigenden Einfluss hat. Erfindungsgemäß wird Wasser unter sehr geringem Druck verdampft, durch eine oder mehrere hintereinander angeordnete Strömungsmaschinen verdichtet und wieder verflüssigt zu Wasser. Die transportiere Energie wird zum Heizen benutzt. Erfindungsgemäß wird eine Wärmepumpe verwendet, die bevorzugt ein offenes System darstellt. Offenes System bedeutet hier, dass Grundwasser oder ein anderes verfügbares Wärmeenergie-tragendes wässriges Medium unter geringem Druck verdampft, verdichtet und verflüssigt wird. Das Wasser wird direkt als Arbeitsmittel verwendet. Die enthaltene Energie wird also nicht an ein geschlossenes System übertragen. Das verflüssigte Wasser wird vorzugsweise direkt im Heizungssystem verwendet und anschließend dem Grundwasser wieder zugeführt. Um das Heizsystem kapazitiv zu entkoppeln, kann es ebenso über einen Wärmetauscher abgeschlossen werden.The heat pump according to the invention thus serves for efficient heat supply of buildings and no longer requires working equipment that has a global climate-damaging influence. According to the invention, water is evaporated under very low pressure, compressed by one or more turbomachines arranged one behind the other and liquefied again into water. The transporting energy is used for heating. According to the invention, a heat pump is used, which is preferably an open system. Open system here means that groundwater or other available thermal energy-carrying aqueous medium is evaporated, compacted and liquefied under low pressure. The water is used directly as a working medium. The contained energy is therefore not transferred to a closed system. The liquefied water is preferably used directly in the heating system and then fed back to the groundwater. To decouple the heating system capacitively, it can also be completed via a heat exchanger.
Die Effizienz und Nützlichkeit der vorliegenden Erfindung wird anhand eines Zahlenbeispiels dargestellt. Wenn von einem Jahreswärmebedarf von 30.000 kWh ausgegangen wird, müssen erfindungsgemäß hierfür etwa maximal 3750 kWh elektrischer Strom für den Betrieb der Strömungsmaschine aufgewendet werden, da die Strömungsmaschine nur etwa ein Achtel des gesamten Wärmebedarfs liefern muss.The efficiency and usefulness of the present invention will be illustrated by way of a numerical example. If an annual heat requirement of 30,000 kWh is assumed, according to the invention about a maximum of 3750 kWh of electric power must be expended for the operation of the turbomachine, since the turbomachine only has to supply about one eighth of the total heat requirement.
Das Achtel ergibt sich daher, dass nur bei extremster Kälte ein Sechstel aufgewendet werden muss, und z. B. bei Übergangstemperaturen wie im März oder Ende Oktober der Wirkungsgrad bis auf einen Wert größer 12 steigen kann, so dass im Mittel über das Jahr maximal ein Achtel aufgewendet werden muss.The eighth comes from the fact that only in the most extreme cold a sixth must be spent, and z. B. at transition temperatures such as in March or the end of October, the efficiency can rise to a value greater than 12, so that a maximum of one-eighth must be spent on average over the year.
Bei Stromkosten von etwa 10 Cent pro kWh, die für Strom erreicht werden können, wenn Strom gekauft wird, für den das Kraftwerk keine Unterbrechungsfreiheit garantieren muss, entspricht dies etwa jährlichen Kosten von 375 Euro. Wenn man 30.000 kWh mit Öl erzeugen möchte, würde man etwa 4000 l brauchen, was bei derzeitigen Ölkosten, die in Zukunft sehr wahrscheinlich nicht fallen werden, einem Preis von 2800 Euro entsprechen würde. Erfindungsgemäß kann man daher pro Jahr 2425 Euro einsparen! Ferner sei auch darauf hingewiesen, dass im Vergleich zur Verbrennung von Öl oder Gas zu Zwecken der Heizung durch das erfindungsgemäße Konzept bis zu 70 % der Menge an freigesetztem CO2 eingespart wird.With electricity costs of about 10 cents per kWh, which can be achieved for electricity when electricity is purchased, for which the power plant does not have to guarantee freedom of interruption, this corresponds to an annual cost of about 375 euros. If you want to produce 30,000 kWh of oil, you would need about 4,000 liters, which would be equivalent to a price of 2800 euros given current oil costs, which are unlikely to fall in the future. According to the invention, one can therefore save 2425 euros per year! It should also be noted that compared to the combustion of oil or gas for heating purposes by the inventive concept, up to 70% of the amount of released CO 2 is saved.
Zur Reduktion der Herstellungskosten und auch zur Reduktion der Wartungs- und Montagekosten wird es bevorzugt, die Gehäuse des Verdampfers, des Verdichters und/oder des Verflüssigers und auch besonders das Radialrad der Strömungsmaschine aus Kunststoff und insbesondere aus Spritzguss-Kunststoff auszuführen. Kunststoff eignet sich gut, da Kunststoff bezüglich Wasser korrosionsresistent ist und erfindungsgemäß vorteilhafterweise die maximalen Temperaturen im Vergleich zu konventionellen Heizungen deutlich unter den Verformungstemperaturen einsetzbarer Kunststoffe liegen. Ferner ist die Montage besonders einfach, da im System aus Verdampfer, Verdichter und Verflüssiger Unterdruck herrscht. Damit werden an die Dichtungen wesentlich weniger Anforderungen gestellt, da der gesamte Atmosphärendruck dabei hilft, die Gehäuse dicht zu halten. Kunststoff eignet sich ferner besonders gut, da an keiner Stelle im erfindungsgemäßen System hohe Temperaturen auftreten, die den Einsatz von teuren Spezialkunststoffen, Metall oder Keramik erforderlich machen würden. Durch Kunststoff-spritzguss kann auch die Form des Radialrads beliebig optimiert und dennoch trotz komplizierter Form einfach und kostengünstig hergestellt werden.In order to reduce the manufacturing costs and also to reduce the maintenance and assembly costs, it is preferable to carry out the housing of the evaporator, the compressor and / or the condenser and also especially the radial impeller of the fluid machine made of plastic and in particular of injection-molded plastic. Plastic is well suited, since plastic is corrosion-resistant with respect to water and, according to the invention, advantageously the maximum temperatures are significantly below the deformation temperatures of usable plastics in comparison with conventional heaters. Furthermore, the assembly is particularly simple, since there is negative pressure in the system of evaporator, compressor and condenser. As a result, the requirements for the gaskets are significantly reduced because the entire atmospheric pressure helps to keep the housings tight. Plastic is also particularly well, since at no point high temperatures occur in the system according to the invention, which would require the use of expensive special plastics, metal or ceramic. By plastic injection molding and the shape of the radial wheel can be arbitrarily optimized and yet easily and inexpensively manufactured in spite of complicated shape.
Claims (9)
- A heat pump comprising:an evaporator device (10) comprising:a water evaporator (10) for evaporating water as a working liquid to generate a working vapor, the water evaporator comprising an evaporation chamber (100) and being adapted to generate an evaporation pressure of less than 20 hPa within the evaporation chamber, so that the water will evaporate at temperatures below 18°C,a compressor (16) coupled to the evaporator (10) for compressing the working vapor, the compressor being adapted as a continuous flow machine and further being adapted to compress the working vapor to a working pressure of more than 5 hPa above the evaporation pressure; anda liquefier (18) for liquefying a compressed working vapor, the liquefier being adapted to output a heat which has been acquired during the liquefaction to a heating system,characterized in that the water evaporator (10) further comprises
an expander (108) which expands within the evaporation chamber to at least three times a diameter of a feed to the evaporation chamber;
a reception apparatus (110) adapted to receive any working liquid overflowing over an edge of the expander (108); and
a drain (112) adapted to carry off the overflowing working liquid. - The heat pump as claimed in claim 1, wherein the evaporator device comprises a turbine (150), via which a pressure of an upstreaming working fluid is reduced, and which extracts energy from the working liquid in the process, the turbine (150) further being operatively coupled to a pump (152) to bring a downstreaming working liquid from the pressure present within the evaporation chamber to the pressure of the upstreaming working fluid, the operative coupling (154) being adapted such that the pump (152) uses at least part of the energy the turbine has extracted.
- The heat pump as claimed in claim 1, wherein the drain (112) is coupled to a flow controller (114), the flow controller (114) being controllable to maintain a level of the overflowing working liquid within the reception apparatus (110) within a predefined range.
- The heat pump as claimed in one of the preceding claims, wherein the evaporator device (10) comprises a gas separator adapted to remove at least part of a gas dissolved in the water to be evaporated from the water to be evaporated, so that the removed part of the gas is not sucked in by the compressor via the evaporation chamber.
- The heat pump as claimed in claim 4, wherein the gas separator is arranged to feed the removed part of the gas to non-evaporated water so that the gas is transported off by the non-evaporated water.
- The heat pump as claimed in claim 1 or 2, wherein the evaporator device (10) further comprises:an expander (200) which expands, within the evaporation chamber, to at least three times a diameter of the drain (112) outside the evaporation chamber;a reception apparatus adapted to receive the working liquid fed to the evaporation chamber; andan inflow to supply the reception apparatus with ground water;wherein the expander is arranged within the evaporation chamber such that the working fluid flows off, over an edge of the expander comprising a large diameter, to an area of the expander comprising a low diameter, and from there to a drain.
- The heat pump as claimed in claim 2, wherein the liquefier (18) comprises a drain (22) for draining off liquefied working liquid, the drain being coupled, at a coupling position (194), to the riser pipe (102) or to a backflow pipe (113), where a liquid pressure within the riser pipe or the backflow pipe (113) is smaller than or equal to a pressure present at the drain (22).
- The heat pump as claimed in claim 2 or 7, wherein the liquefier (18) comprises a drain (22) for draining off liquefied working liquid, the drain being coupled, at a coupling position (194), to the riser pipe (102) or to a backflow pipe (113), a pressure compensator (192) being arranged between the drain (22) from the liquefier (18) and the coupling position (194), the pressure compensator (192) being adapted to control a pressure of the water drained off from the liquefier (18) such that the water will enter into the riser pipe (102) or into the backflow pipe (192).
- A method of pumping heat, comprising:evaporating (10) water as a working liquid by a water evaporator (10) to generate a working vapor, the working vapor being generated at an evaporation pressure of less than 20 hPa, so that the water will evaporate at temperatures below 18°C, the water evaporator comprising
an expander (108) which expands in the evaporation chamber to at least three times a diameter of a feed line to the evaporation chamber;
a reception apparatus (110) adapted to receive any working liquid overflowing over an edge of the expander; and
a drain (112) adapted to carry off the overflowing working liquid;compressing (16) the working vapor in terms of flow so as to compress the working vapor to a working pressure of more than 5 hPa above the evaporation pressure; andliquefying (18) a compressed working vapor to output a heat which has been acquired during the liquefaction to a heating system.
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
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EP11158798A EP2341301A3 (en) | 2006-04-04 | 2006-04-04 | Heat pump |
EP10189256.0A EP2290305B1 (en) | 2006-04-04 | 2006-04-04 | Evaporator |
EP11158793.7A EP2343489B1 (en) | 2006-04-04 | 2006-04-04 | Heat pump |
EP11158786.1A EP2341300B1 (en) | 2006-04-04 | 2006-04-04 | Heat pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/EP2006/003061 WO2007118482A1 (en) | 2006-04-04 | 2006-04-04 | Heat pump |
DE202006005461U DE202006005461U1 (en) | 2006-04-04 | 2006-04-04 | Heat pump for pumping heat, has compressor implemented as turbo machine and designed to compress operating steam at operating pressure higher than five hecto-Pascal above evaporation pressure |
Related Child Applications (7)
Application Number | Title | Priority Date | Filing Date |
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EP11158786.1A Division EP2341300B1 (en) | 2006-04-04 | 2006-04-04 | Heat pump |
EP10189256.0A Division EP2290305B1 (en) | 2006-04-04 | 2006-04-04 | Evaporator |
EP11158793.7A Division EP2343489B1 (en) | 2006-04-04 | 2006-04-04 | Heat pump |
EP10189256.0 Division-Into | 2010-10-28 | ||
EP11158793.7 Division-Into | 2011-03-18 | ||
EP11158798.6 Division-Into | 2011-03-18 | ||
EP11158786.1 Division-Into | 2011-03-18 |
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EP2016349A1 EP2016349A1 (en) | 2009-01-21 |
EP2016349B1 true EP2016349B1 (en) | 2011-05-04 |
Family
ID=39166769
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Application Number | Title | Priority Date | Filing Date |
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EP11158798A Withdrawn EP2341301A3 (en) | 2006-04-04 | 2006-04-04 | Heat pump |
EP10189256.0A Active EP2290305B1 (en) | 2006-04-04 | 2006-04-04 | Evaporator |
EP06724016A Active EP2016349B1 (en) | 2006-04-04 | 2006-04-04 | Heat pump |
EP11158786.1A Active EP2341300B1 (en) | 2006-04-04 | 2006-04-04 | Heat pump |
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Application Number | Title | Priority Date | Filing Date |
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EP11158798A Withdrawn EP2341301A3 (en) | 2006-04-04 | 2006-04-04 | Heat pump |
EP10189256.0A Active EP2290305B1 (en) | 2006-04-04 | 2006-04-04 | Evaporator |
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Application Number | Title | Priority Date | Filing Date |
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EP11158786.1A Active EP2341300B1 (en) | 2006-04-04 | 2006-04-04 | Heat pump |
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US (3) | US7841201B2 (en) |
EP (4) | EP2341301A3 (en) |
JP (1) | JP5216759B2 (en) |
DE (2) | DE202006005461U1 (en) |
WO (1) | WO2007118482A1 (en) |
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Also Published As
Publication number | Publication date |
---|---|
US20160109139A1 (en) | 2016-04-21 |
EP2016349A1 (en) | 2009-01-21 |
US10337746B2 (en) | 2019-07-02 |
US7841201B2 (en) | 2010-11-30 |
EP2341300A1 (en) | 2011-07-06 |
EP2341301A3 (en) | 2011-10-05 |
EP2290305A1 (en) | 2011-03-02 |
DE202006005461U1 (en) | 2007-08-16 |
DE502006009456D1 (en) | 2011-06-16 |
JP5216759B2 (en) | 2013-06-19 |
EP2290305B1 (en) | 2017-09-06 |
US20070245759A1 (en) | 2007-10-25 |
EP2341300B1 (en) | 2017-09-06 |
JP2009532655A (en) | 2009-09-10 |
WO2007118482A1 (en) | 2007-10-25 |
EP2341301A2 (en) | 2011-07-06 |
US20110036100A1 (en) | 2011-02-17 |
US9222483B2 (en) | 2015-12-29 |
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